Plate sheet and heat exchanger

Abstract

The heat exchanger is provided with a middle area and end areas, the end areas are located on the two sides of the middle area in the length direction of the heat exchanger, the heat exchanger comprises at least two plates stacked in the height direction of the heat exchanger, and the heat exchanger is provided with at least one inter-plate channel. The same kind of fluid can circulate in the same kind of inter-plate channels, the inter-plate channels are located between the adjacent plates, each inter-plate channel comprises at least two sub-channels arranged in the height direction of the heat exchanger, and in the same kind of inter-plate channels, at least one sub-channel is provided with a bypass flow channel, and the bypass flow channels are located in the end areas; and the distribution performance of the fluid in the inter-plate channel is improved.

Description

Technical Field

[0001] The present application relates to the field of heat exchange technology, and in particular to a plate and a heat exchanger. Background Art

[0002] The heat exchanger includes a plurality of plates, and heat exchange channels are formed between adjacent plates. Fluid can flow through the heat exchange channels to exchange heat with external devices of the heat exchanger. How to improve the distribution performance of fluid in the channels between the plates is a technical problem that needs to be solved urgently. Summary of the invention

[0003] The purpose of the present application is to provide a plate and a heat exchanger, which are conducive to improving the distribution performance of the fluid in the channels between the plates.

[0004] To achieve the above purpose, an implementation method of the present application adopts the following technical solution:

[0005] A heat exchanger, the heat exchanger having a middle area and an end area, along the length direction of the heat exchanger, the end areas are located on both sides of the middle area, the heat exchanger comprises at least two plates stacked along the height direction of the heat exchanger, the heat exchanger has at least one inter-plate channel, the same inter-plate channels can flow the same fluid, the inter-plate channels are located between adjacent plates, the same inter-plate channels comprise at least two sub-channels arranged along the height direction of the heat exchanger, in the same inter-plate channels, at least one sub-channel has a bypass flow channel, the bypass flow channel is located in the end area.

[0006] According to the heat exchanger provided in the embodiment of the present application, at least one of the sub-channels has a bypass flow channel, and the bypass flow channel is located in the end area, so that when the fluid flows through at least one sub-channel, the fluid can be better distributed under the action of the bypass channel, thereby increasing the flow area of ​​the fluid in the heat exchanger and increasing the heat exchange area of ​​the heat exchanger.

[0007] On the other hand, an embodiment of the present application also provides a heat exchanger, which has a middle area. The heat exchanger includes at least two plates, and the plates are stacked along the height direction of the heat exchanger. The plates include a plurality of protrusion structures, and at least a part of the protrusion structures are scattered in the middle area. The protrusion structures located in the middle area are arranged in an array along a first direction and a second direction, and the first direction intersects with the second direction. One of the angles between the first direction and the second direction is defined as α1, and α1 is toward the length direction of the heat exchanger, and α1 is less than 90 degrees.

[0008] According to the heat exchanger provided in the embodiment of the present application, a plurality of protrusion structures arranged in an array along a first direction and a second direction are provided on the plate, so that the fluid can be distributed easily, and the angle α between the first direction and the second direction toward the length direction of the heat exchanger is set to be less than 90 degrees. At this time, along the length direction of the heat exchanger, the angle between the first direction and the second direction is small, so that the fluid has a smaller flow resistance when flowing along the length direction of the heat exchanger, which facilitates increasing the flow path of the fluid in the length direction of the heat exchanger.

[0009] One embodiment of the present application provides a plate, including a rib portion, which is protruding from the plate. Along the length direction of the plate, the rib portion extends from one side of the plate to the opposite other side. Along the extension direction of the rib portion, a connecting portion is provided between the rib portion and one side of the plate. The plate includes a corner hole. Along the length direction of the plate, the corner hole is close to the other side of the plate relative to the connecting portion.

[0010] In the above technical solution, along the length direction of the plate, the connecting portion is close to one side of the plate, and the corner hole is close to the other side of the plate relative to the connecting portion. The connecting portions on both sides of the plate at least partially overlap, and the flow areas of the first fluid and the second fluid at least partially overlap, thereby increasing the heat exchange area of ​​the first fluid and the second fluid, thereby enhancing the heat exchange effect.

[0011] One embodiment of the present application provides a heat exchanger, including the above-mentioned plate, wherein a plurality of plates are stacked, a first inter-plate channel or a second inter-plate channel is provided between the plate and adjacent plates, the ribs abut against adjacent plates, the connecting portions connect the areas on both sides of the ribs, and the connecting portions on both sides of the plates at least partially overlap.

[0012] In the above technical solution, along the direction perpendicular to the plate, since the connecting parts located on both sides of the plate at least partially overlap, the flow areas of the first fluid and the second fluid at least partially overlap, thereby increasing the heat exchange area of ​​the first fluid and the second fluid, thereby enhancing the heat exchange effect.

[0013] Another embodiment of the present application provides a heat exchanger, comprising a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first substrate, wherein the first protrusions protrude relative to the first substrate toward the second plate; wherein the first plate comprises a first rib, wherein the first rib protrudes relative to the first substrate toward the second plate, and wherein a protruding direction of the first rib is consistent with a protruding direction of the first protrusion; wherein the plurality of first protrusions comprise a first group of first protrusions and a second group of first protrusions, wherein the first group of first protrusions and the second group of first protrusions are both composed of first protrusions adjacent to the first rib; and wherein a direction perpendicular to an extension direction of the first rib is defined as a third direction, wherein along the third direction, the first group of first protrusions are located on one side of the first rib, and the second group of first protrusions are located on the other side of the first rib, and wherein along the third direction, the first group of first protrusions are closer to the first rib than the second group of first protrusions.

[0014] In the heat exchanger provided in the embodiment of the present application, along the third direction, the first group of first protrusions is closer to the first rib than the second group of first protrusions, so that the flow resistance of the channel formed between the first group of first protrusions and the first rib is smaller than the flow resistance of the channel formed between the second group of first protrusions and the first rib, thereby making the bypass flow formed between the first group of first protrusions and the first rib relatively reduced, so that the fluid flows more to the channels between the first protrusions, thereby improving the heat exchange performance of the heat exchanger.

[0015] Another embodiment of the present application provides a heat exchanger, comprising a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first substrate, wherein the first protrusions protrude relative to the first substrate toward the second plate; wherein the first plate comprises a first rib, wherein the first rib protrudes relative to the first substrate toward the second plate, and the protruding direction of the first rib is consistent with the protruding direction of the first protrusion; wherein the plurality of first protrusions comprise a first group of first protrusions and a second group of first protrusions, wherein the first group of first protrusions and the second group of first protrusions are both composed of first protrusions adjacent to the first rib; wherein a direction perpendicular to an extension direction of the first rib is defined as a third direction, wherein along the third direction, the first group of first protrusions are located on one side of the first rib, and the second group of first protrusions are located on the other side of the first rib; and wherein along the third direction, a width of the first group of first protrusions is greater than a width of the second group of first protrusions.

[0016] In the heat exchanger provided in the embodiment of the present application, along the third direction, the width of the first group of first protrusions is greater than the width of the second group of first protrusions. The relatively wider first group of first protrusions has a stronger fluid resistance and can further reduce the fluid flow passing through the first group of first protrusions and the first rib.

[0017] One implementation of the present application adopts the following technical solution:

[0018] A heat exchanger comprises a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first base plate, wherein the first protrusions protrude relative to the first base plate toward the second plate;

[0019] The first plate includes a first rib and a connecting portion, wherein the first rib is located on the first substrate. Along the length direction of the heat exchanger, the first rib extends from one end of the first plate to the other end, and the connecting portion is located between the first rib and the first protrusion. The connecting portion protrudes toward the second plate relative to the first substrate. Along the height direction of the heat exchanger, at least part of the first protrusion is close to the second plate relative to the connecting portion.

[0020] In an embodiment provided in the present application, the first plate includes a connecting portion, which is located between the first rib and the first convex portion, and can relatively increase the flow resistance of the channel between the plates, increase the heat exchange area of ​​the channel between the plates, and improve the heat exchange efficiency.

[0021] The present application provides a heat exchanger, comprising a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first substrate, wherein the first protrusions protrude relative to the first substrate toward the second plate, and wherein the second plate comprises a second substrate and a plurality of second protrusions;

[0022] The heat exchanger has a reinforcing rib, which is located on the first plate, protrudes toward the second plate relative to the first substrate, and abuts against and is fixedly connected to the second plate; and / or, the reinforcing rib is located on the second plate, protrudes toward the first plate relative to the second substrate, and abuts against and is fixedly connected to the first plate.

[0023] In one embodiment provided in the present application, the heat exchanger has reinforcing ribs, and the provision of the reinforcing ribs 9 helps to improve the strength of the heat exchanger during welding.

[0024] The present application provides a heat exchanger, wherein the first plate includes a first flow portion, and the second plate includes a second flow portion, and the first flow portion and the second flow portion are arranged opposite to each other along the height direction of the heat exchanger; the second plate includes a welding portion, and the welding portion is located at the second flow portion, and the welding portion includes a first sub-welding portion and a second sub-welding portion; the second plate includes a second substrate, and along the height direction of the heat exchanger, the first sub-welding portion and the second sub-welding portion protrude outward in opposite directions relative to the second substrate, and the first sub-welding portion is fixedly connected to the first plate, and the second sub-welding portion is fixedly connected to another first plate.

[0025] In an embodiment provided in the present application, the second plate has a welding portion, which is beneficial to enhancing the structural strength of the heat exchanger, and the welding portion is welded and fixed to the adjacent first plate, further increasing the structural strength, and the structure of the welding portion is simple.

[0026] One implementation of the present application adopts the following technical solution:

[0027] A heat exchanger includes a first plate and a second plate, with a first inter-plate channel between the first plate and the second plate, characterized in that the first plate includes a first rib, the first rib protrudes toward the second plate, the first rib extends in a curved shape along the length direction of the first plate, and the first rib and the plate surface of the second plate are welded and fixed.

[0028] A heat exchanger includes a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate includes a first rib, wherein the first rib protrudes toward the second plate, wherein the first rib and the plate surface of the second plate are welded and fixed, and wherein the first plate includes a first protrusion, wherein the first protrusion protrudes toward the second plate; wherein the first protrusion is arranged along an F direction, and a portion of the first rib extends parallel to the F direction.

[0029] A heat exchanger includes a first plate, wherein the first plate includes a first substrate and a plurality of first high segments, wherein the first high segments are protruded relative to the first substrate, and along the width direction of the heat exchanger, the distance between the center points of two adjacent first high segments is d1, and the ratio of d1 to the height H2 of the top of the first high segment from the plate surface of the first substrate is 1.5 to 6.

[0030] In one embodiment provided in the present application, a heat exchanger includes a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, and wherein the first plate includes a first rib, wherein the first rib protrudes toward the second plate, and the first rib extends in a curved shape along the length direction of the first plate, and the first rib and the plate surface of the second plate are welded and fixed; such an arrangement can make the shape of the second rib consistent with the flow direction of the coolant, thereby avoiding the second rib obstructing the flow of the coolant, reducing the flow resistance of the coolant flow, making the coolant flow smoother, and improving the heat exchange effect between the coolant and the refrigerant.

[0031] A heat exchanger comprises a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a first rib, wherein the first rib protrudes toward the second plate, wherein the first rib and the plate surface of the second plate are welded and fixed, and wherein the first plate comprises a first protrusion, wherein the first protrusion protrudes toward the second plate; wherein the first protrusion is arranged along the F direction, and a part of the first rib extends parallel to the F direction; thus, the flow path of the refrigerant near both sides of the first rib is consistent with the flow path between the first protrusion, which is conducive to reducing the resistance to the flow of the refrigerant, making the flow of the refrigerant smoother, and making the refrigerant and the coolant have a higher heat exchange effect.

[0032] A heat exchanger comprises a first plate, wherein the first plate comprises a first substrate and a plurality of first high segments, wherein the first high segments are arranged to be raised relative to the first substrate, and along the width direction of the heat exchanger, the distance between the center points of two adjacent first high segments is d1, and the ratio of d1 to the height H2 of the top of the first high segment from the plate surface of the first substrate is 1.5 to 6; through each of the above schemes, the heat exchange effect of the heat exchanger is improved; in this way, the first high segments can be arranged relatively densely, which is conducive to increasing the heat exchange area between the refrigerant and the coolant and improving the heat exchange effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 It is a schematic diagram of a partial decomposition structure of a heat exchanger provided by an embodiment of the present invention;

[0034] Figure 2 It is a front view structural schematic diagram of a heat exchanger provided by an embodiment of the present invention;

[0035] Figure 3 is a front view structural schematic diagram of one side of a first plate provided by an embodiment of the present invention;

[0036] Figure 4 is a front view structural schematic diagram of one side of a first plate provided by another embodiment of the present invention;

[0037] Figure 5 is a front view structural schematic diagram of one side of a second plate provided by an embodiment of the present invention;

[0038] Figure 6 is a front view structural schematic diagram of one side of a second plate provided by another embodiment of the present invention;

[0039] Figure 7 yes Figure 1 A schematic diagram of a partial cross-sectional structure of one side of a heat exchanger in the longitudinal direction is shown in FIG.

[0040] Figure 8 yes Figure 1 A schematic diagram of a partial cross-sectional structure of the other side of the length direction of a heat exchanger shown in FIG.

[0041] Fig. 9 yes Figure 1 A schematic diagram of a partial cross-sectional structure of a heat exchanger along the length direction is shown in FIG.

[0042] Fig.10 yes Figure 1 Another partial cross-sectional structural schematic diagram of a heat exchanger along the length direction is shown in FIG.

[0043] Fig.11 A schematic diagram of the exploded structure of the first plate and the second plate of one embodiment;

[0044] Fig.12 yes Figure 4 A schematic diagram of a three-dimensional structure of a first plate is shown in FIG.

[0045] Fig.13 Fig.11 Another exploded structural schematic diagram of the first plate and the second plate is shown in FIG.

[0046] Fig.14 yes Figure 5 A partially enlarged structural schematic diagram of a second plate is shown in FIG.

[0047] Fig.15 yes Figure 2 A schematic diagram of a partial cross-sectional structure of a heat exchanger along the MM direction is shown in FIG.

[0048] Fig.16 yes Figure 2 A schematic diagram of a partial cross-sectional structure of a heat exchanger shown in another position;

[0049] Fig.17 yes Figure 4 A schematic diagram of a partial structure of a first plate shown in FIG.

[0050] Fig.18 is a schematic diagram of a partial arrangement structure of a first convex portion provided by an embodiment of the present invention;

[0051] Fig.19 is a partial schematic diagram of a first convex portion provided by an embodiment of the present invention;

[0052] Fig. 20 is a schematic diagram of a partial arrangement structure of a second convex portion provided by an embodiment of the present invention;

[0053] Fig.21 is a partial schematic diagram of a second convex portion provided by an embodiment of the present invention;

[0054] Fig. 22 A schematic diagram of the exploded structure of the first plate and the second plate in the heat exchanger is shown;

[0055] Fig.23 Shows Fig. 22 The schematic diagram of the structure of the first plate at an angle is shown;

[0056] Fig.24 Shows Fig. 22 The schematic diagram of the partial three-dimensional structure of the second plate at position C is shown;

[0057] Fig.25 Shows Fig.23 The schematic diagram of the local structure of the first plate at position A is shown;

[0058] Fig.26 Shows Fig.23 The schematic diagram of the local structure of the first plate at position B is shown;

[0059] Fig. 27 Shows Fig.23 The schematic diagram of the local structure of the first plate at position B is shown;

[0060] Fig.28 It is a three-dimensional structural schematic diagram of a first embodiment of the heat exchanger provided by the present application from one viewing angle;

[0061] Fig.29 yes Fig.28 A schematic diagram of a three-dimensional structure of the heat exchanger from another perspective;

[0062] Fig.30 yes Fig.28 Schematic diagram of the cross-sectional structure of the heat exchanger;

[0063] Fig.31 yes Fig.28 A schematic cross-sectional structure diagram of another embodiment of a heat exchanger;

[0064] Fig.32This is a schematic diagram of the structure of the plate before the heat exchanger of the present application is assembled;

[0065] Fig.33 It is a structural schematic diagram of the first embodiment of the rib portion in the present application;

[0066] Fig.34 It is a structural schematic diagram of a second embodiment of the rib portion in the present application;

[0067] Fig.35 It is a schematic diagram of the assembly structure of the first embodiment of the rib part in the present application;

[0068] Fig.36 It is a schematic diagram of the assembly structure of the second embodiment of the rib portion in the present application;

[0069] Fig.37 It is a three-dimensional structural schematic diagram of a first embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0070] Fig.38 It is a structural schematic diagram of a second embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0071] Fig.39 It is a structural schematic diagram of a third embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0072] Fig.40 It is a structural schematic diagram of a fourth embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0073] Fig.41 It is a structural schematic diagram of a fifth embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0074] Fig.42 It is a structural schematic diagram of a sixth embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0075] Fig.43 It is a structural schematic diagram of a seventh embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0076] Fig.44 It is a structural schematic diagram of an eighth embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0077] Fig.45 It is a structural schematic diagram of a ninth embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0078] Fig.46 It is a structural schematic diagram of a tenth embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0079] Fig.47 It is a structural schematic diagram of an eleventh embodiment of the first hole channel, the second hole channel, the third hole channel and the fourth hole channel of the plate of the present application;

[0080] Fig.48 It is a three-dimensional structural schematic diagram of a heat exchanger provided by the present application from one perspective;

[0081] Fig.49 is a three-dimensional structural schematic diagram of the heat exchanger provided by the present application from another perspective;

[0082] Fig.50 yes Fig.48 A three-dimensional structural schematic diagram of a local structure of a heat exchanger from one perspective;

[0083] Fig.51 yes Fig.50 A schematic cross-sectional structure diagram of a local structure of the heat exchanger along A7-A7;

[0084] Fig.52 yes Fig.50 An exploded structural diagram of a local structure of a heat exchanger;

[0085] Fig.53 yes Fig.52 A schematic diagram of a three-dimensional structure of the first plate from one viewing angle;

[0086] Fig.54 yes Fig.52 A schematic diagram of the three-dimensional structure of the first plate from another perspective;

[0087] Fig.55 yes Fig.54 A schematic diagram of the enlarged structure of the middle part A;

[0088] Fig.56 yes Fig.52 A schematic diagram of the three-dimensional structure of the second plate from one viewing angle;

[0089] Fig.57 yes Fig.52 A schematic diagram of the three-dimensional structure of the second plate from another perspective;

[0090] Fig.58 yes Fig.57 A schematic diagram of the enlarged structure of the middle B part;

[0091] Fig.59 yes Fig.48 Another partial structural schematic diagram of the heat exchanger;

[0092] Fig.60 yes Fig.59 A schematic cross-sectional view of another local structure of the middle heat exchanger along A6-A6;

[0093] Fig.61 yes Fig.59 A schematic structural diagram of a combined structure of a first rib portion and a second rib portion of a heat exchanger;

[0094] Fig.62 yes Fig.57 A schematic structural diagram of a partial structure of a second plate of a heat exchanger;

[0095] Fig.63 yes Fig.62 A schematic cross-sectional view of the partial structure of the second plate of the middle heat exchanger along the A1-A1 plane;

[0096] Fig.64 yes Fig.57 A schematic diagram of the partial structure of the second plate of the middle heat exchanger;

[0097] Fig.65 yes Fig.64 A schematic diagram of the cross-sectional structure along the middle A2-A2 plane;

[0098] Fig.66 is a partial schematic diagram of a first plate of a heat exchanger;

[0099] Fig.67 yes Fig.66 A schematic diagram of the cross-sectional structure of the A4-A4 surface;

[0100] Fig.68 yes Fig.66 A schematic diagram of the cross-sectional structure of the A5-A5 surface;

[0101] Fig.69 is a structural schematic diagram of a connection portion of a first plate of a heat exchanger;

[0102] Fig.70 yes Fig.69 A schematic diagram of the cross-sectional structure of the A3-A3 plane;

[0103] Fig.71 yes Fig.54 A schematic structural diagram of a local structure of the first plate;

[0104] Fig.72 yes Fig.71 A schematic cross-sectional view of the local structure of the first plate along the BB plane;

[0105] Fig.73 yes Fig.71 Schematic diagram of the cross-sectional structure of the local structure of the first plate along the CC plane. DETAILED DESCRIPTION

[0106] The present application is further described below with reference to the accompanying drawings and specific embodiments:

[0107] like Figures 1 to 21 As shown, an embodiment of the present invention provides a heat exchanger 100, which has a middle area 105 and an end area 106. Along the length direction of the heat exchanger 100, the end areas 106 are located on both sides of the middle area 105. The heat exchanger 100 includes at least two plates 5 stacked along the height direction of the heat exchanger 100. The heat exchanger 100 has at least one inter-plate channel S0. The same inter-plate channels S0 can flow the same fluid. The inter-plate channels S0 are located between adjacent plates 5. The same inter-plate channels S0 include at least two sub-channels S01 arranged along the height direction of the heat exchanger 100. In the same inter-plate channels S0, at least one sub-channel S01 has a bypass flow channel BS, and the bypass flow channel BS is located in the end area 106. Through the above-mentioned arrangement, the fluid can be better distributed under the action of the bypass channel BS when flowing through at least one sub-channel S01. For example, the fluid can flow to the end area 106 or close to the end area 106 under the action of the bypass channel BS, thereby increasing the flow area of ​​the fluid in the heat exchanger 100, increasing the heat exchange area of ​​the heat exchanger 100, and improving the utilization rate of the heat exchanger 100.

[0108] Specifically, in the embodiment of the present invention, the heat exchanger 100 includes a plurality of plates 5, and the plurality of plates 5 are stacked and arranged along the height direction of the heat exchanger. In this embodiment, the heat exchanger 100 has a first inter-plate channel S1 and a second inter-plate channel S2, and the first inter-plate channel S1 and the second inter-plate channel S2 are alternately arranged along the height direction of the heat exchanger 100. The first inter-plate channel S1 and the second inter-plate channel S2 each include a plurality of sub-channels S01, and each sub-channel S01 is located between two adjacent plates 5. Specifically, there is a first inter-plate channel S1 between the plate 5 and the plate 5 on the adjacent side, that is, there is a sub-channel S01 between the plate 5 and the plate 5 on the adjacent side, and there is a second inter-plate channel S2 between the plate 5 and the plate 5 on the adjacent other side, that is, there is a sub-channel S01 between the plate 5 and the plate 5 on the adjacent other side, the first inter-plate channel S1 and the second inter-plate channel S2 are alternately arranged, and the first inter-plate channel S1 and the second inter-plate channel S2 are fluid-isolated, that is, the first inter-plate channel S1 is for the flow of the first fluid, and the second inter-plate channel S2 is for the flow of the second fluid, and the first fluid and the second fluid perform heat exchange. The first inter-plate channel S1 and the second inter-plate channel S2 are alternately arranged, so that the area for heat exchange between the first fluid and the second fluid is large, and the heat exchange effect of the heat exchanger 100 is relatively good.

[0109] In other embodiments, the first inter-plate channel S1 may be provided between the plate 5 and the plate 5 on the adjacent side, and the first inter-plate channel S1 may be provided between the plate 5 and the plate 5 on the adjacent other side, and the second inter-plate channel S2 may be provided between the next layer of plates 5, that is, two layers of first inter-plate channels S1 may be provided continuously, and then one layer of second inter-plate channels S2 may be provided, so that heat exchange between the first fluid and the second fluid may be achieved. In other embodiments, two or more layers of second inter-plate channels S2 may be provided continuously, and then several layers of first inter-plate channels S1 may be provided.

[0110] In this embodiment, the second fluid refers to the coolant, which is mainly a coolant, such as cooling water or cooling oil. The first fluid in this application refers to the refrigerant, which is mainly a refrigerant, such as R134a, R1234yf, etc. For the convenience of description, the upper and lower parts of the definition direction are as shown in the attached drawings of the specification. Figure 1 The upper and lower directions of the heat exchanger 100 are defined as the upper and lower directions of the heat exchanger 100, and the upper and lower directions only represent relative positions; the height direction, length direction, and width direction of the heat exchanger 100 are defined as the height direction, length direction, and width direction of the heat exchanger 100 in the attached drawings of the specification. Figure 1 In the height direction, length direction, and width direction of the heat exchanger 100, in this application, the height direction of the heat exchanger 100 is consistent with the stacking direction of the plate 5; in this application, the length direction of the plate 5 is consistent with the length direction of the heat exchanger 100, and the width direction of the plate 5 is consistent with the width direction of the heat exchanger 100. In this application, the directions of the adjacent sides are consistent, the directions of the adjacent sides are consistent, the adjacent side refers to the adjacent side facing upward, and the adjacent other side refers to the adjacent side facing downward; or, the adjacent side refers to the adjacent side facing downward, and the adjacent other side refers to the adjacent side facing upward.

[0111] In some embodiments, the plate 5 includes a substrate and a plurality of raised structures TU1, wherein the raised structures TU1 are point wave structures of the plate 5, and the plate 5 may be a stamped part. On one side of the plate 5 in the thickness direction, the raised structures TU1 are raised relative to the substrate, and on the other side of the plate 5 in the thickness direction, the surface of the raised structures TU1 may overlap or be recessed with the surface of the substrate. The middle area 105 of the heat exchanger 100 is the main heat exchange area. In order to allow the fluid to be better filled into the middle area 105, at least a portion of the raised structures TU1 are scattered in the middle area 105. In the same inter-plate channel S0, all the sub-channels S01 have a bypass flow channel BS, and the flow cross-sectional area of ​​the inter-plate channel S0 located in the middle area 105 is smaller than the flow cross-sectional area of ​​the bypass flow channel BS. Through the above arrangement, since the bypass flow channel BS has a small flow cross-sectional area and the bypass flow channel BS is located in the end area 106, according to the flow characteristics of the fluid, the fluid can better pass through the middle area 105 to the bypass flow channel BS, thereby increasing the flow area of ​​the fluid; further, through the arrangement, in the same inter-plate channel S0, all the sub-channels S01 have the bypass flow channel BS, so that the fluid in each layer of the sub-channel S01 can have a larger flow area.

[0112] In this article, the heat exchanger 100 also has a corner hole channel S6, which is located in the end area 106. To facilitate the forming and welding of the plate 5, that is, between the edge of the corner hole channel S6 and the raised structure TU1 along the length direction of the heat exchanger 100, the length of the end area 106 is greater than the length of the area where the corner hole channel S6 is located. Optionally, along the length direction of the heat exchanger 100, the end area 106 can be an area defined by the edge of the length direction of the main body of the heat exchanger 100 to the edge of the raised structure TU1 adjacent to the corner hole channel S6.

[0113] Specifically, Figures 11 to 13 As shown, in some embodiments, the heat exchanger 100 has a corner hole channel S6, which is connected to the same type of inter-plate channel S0. In the same type of inter-plate channel S0, the corner hole channel S6 is located in one end area 106, and the bypass flow channel BS is located in the other end area 106. For a working fluid, such as cooling water or refrigerant, the fluid enters or leaves the heat exchanger 100 from the corner hole channel. Through the above arrangement, when the fluid flows into the inter-plate channel S0 from the corner hole channel S6 of one end area 106, since the bypass flow channel BS of the other end area 106 has a larger fluid cross-sectional area and a smaller flow resistance, when the fluid passes through the middle area 105, the fluid pressure decreases, and the bypass flow channel BS easily "attracts" the fluid to the other end area 106, which is convenient for increasing the flow path of the fluid.

[0114] Further, in some embodiments, in order to increase the welding area and welding strength of the plate 5, the plate 5 includes a main body 3 and a flange 4, the flange 4 is the outer peripheral side surrounding the main body 3, a part of the main body 3 is located in the middle area 105, and another part of the main body 3 is located in the end area 106. In order to increase the flow path of the fluid along the width direction of the heat exchanger 100, at least part of the bypass flow channel BS extends along the width direction of the heat exchanger 100, and optionally, the bypass flow channel BS can extend the entire width direction of the heat exchanger 100 or the bypass flow channel BS can extend more than 70% of the width direction of the heat exchanger 100.

[0115] In a specific implementation, the bypass flow channel BS includes a first flow channel S4, which extends along the width direction of the heat exchanger 100, and the extension distance of the first flow channel S4 is less than or equal to the width of the main body 3. And / or the bypass flow channel BS includes a second flow channel S5, which extends along the length direction of the heat exchanger 100, and at least a part of the second flow channel S5 is located in the end area 106.

[0116] like Figure 4 As shown, in the embodiment of the present invention, the bypass channel BS includes a first channel S4 and a second channel S5, the first channel S4 and the second channel S5 are connected, the second channel S5 is located in the end area 106 as a whole, the second channel S5 runs through one of the end areas 106, and the second channel S5 is adjacent to the convex structure TU1 located in the middle area 105, and the second channel S5 is adjacent to the convex structure TU1. Through the above arrangement, the fluid located in the edge direction of the heat exchanger 100 can flow to the middle area 105, and by setting the bypass channel BS structure, the structural strength of the plate 5 can be increased.

[0117] like Figures 1 to 4 As shown, between two adjacent plates 5 forming the bypass flow channel BS, in the area corresponding to the bypass flow channel BS, one of the plates 5 has a protruding structure, and on the other side away from the protruding structure, the plate 5 has a bypass groove, and the other plate can be a planar structure, and the two plates can define the bypass flow channel BS by welding. Furthermore, by providing a protruding structure on the plate 5, it is convenient to weld the plate with another plate, increase the welding area, and thus improve the welding strength.

[0118] Specifically, in the area corresponding to the bypass channel BS, the plate 5 of the second layer has a protruding structure toward the plate 5 of the third layer, and the plate 5 of the second layer has a groove toward the plate 5 of the first layer, and a bypass channel BS is formed between the plates 5 of the first layer and the plates 5 of the second layer, and the protruding structure of the plates 5 of the second layer is welded to the plates 5 of the third layer, so as to increase the welding strength between the plates 5 of the second layer and the plates 5 of the third layer.

[0119] In some embodiments, the inter-plate channel S0 includes a first inter-plate channel S1 and a second inter-plate channel S2, the first inter-plate channel S1 and the second inter-plate channel S2 are fluid-isolated, cooling water and other fluids can be connected in the first inter-plate channel S1, and refrigerant and other fluids can flow in the second inter-plate channel S2. Correspondingly, the corner hole channel S6 includes a first channel 101, a second channel 102, a third channel 103 and a fourth channel 104, the first channel 101 and the second channel 102 are both connected to the first inter-plate channel S1, and the first channel 101 and the second channel 102 are both located in one end area 106, the third channel 103 and the fourth channel 104 are both connected to the second inter-plate channel S2, and the third channel 103 and the fourth channel 104 are both located in the other end area 106. Through the above arrangement, it is convenient to reasonably arrange the inlet and outlet channels of the two fluids.

[0120] Correspondingly, the subchannel S01 of the first inter-plate channel S1 has a bypass channel BS, and the subchannel S01 of the second inter-plate channel S2 has a bypass channel BS. The bypass channel BS of the first inter-plate channel S1 is defined as a first bypass channel S7, and the bypass channel BS of the second inter-plate channel S2 is defined as a second bypass channel S8. The first bypass channel S7 is located in one end area 106 in the width direction of the heat exchanger 100, and the second bypass channel S8 is located in the other end area 106 in the width direction of the heat exchanger 100. Through the above arrangement, it is convenient to make different types of inter-plate channels S0 have a larger fluid flow area.

[0121] In specific implementation, in the embodiment of the present invention, the end area 106 includes a first area AE1 and a second area AE2, the middle area 105 is located between the first area AE1 and the second area AE2, the first channel 101 and the second channel 102 are both located in the first area AE1, and the third channel 103 and the fourth channel 104 are both located in the second area AE2. For the first inter-plate channel S1, the bypass flow channel BS is located in the second area AE2, and for the second inter-plate channel S2, the bypass flow channel BS is located in the first area AE1. Through the above arrangement, when each working fluid enters the inter-plate channel S0 from the corner hole channel S6, the fluid passes through the middle area 105, and then flows to the end area 106 farther away from the middle area 105 under the action of the bypass flow channel BS. Moreover, since the bypass flow channel BS extends along the width direction of the heat exchanger, the fluid can be better "attracted" in the width direction of the heat exchanger 100, thereby improving the situation in which the fluid flowing through the edge of the width direction of the heat exchanger 100 does not flow or rarely flows to the end area 106, thereby increasing the heat exchange area of ​​the heat exchanger 100.

[0122] Since the corner hole channels S6 for the same fluid are located in the same end area 106, in order to better distribute the fluid, in some embodiments, the plate 5 includes a convex rib TU2, which is located in the middle area of ​​the heat exchanger 100 along the width direction of the heat exchanger 100, and defines a part of the wall of the inter-plate channel S0. The depth of the convex rib TU2 is the same as the depth of the bypass channel BS. The convex rib TU2 extends from the edge of one end area 106 in the length direction of the plate 5 to the other end area 106, or the convex rib TU2 extends from the edge of the wall defining the bypass channel BS to the other end area 106. The projection distance L1 of the convex rib TU2 along the length direction of the plate 5 is less than the length of the main body 3 of the plate 5.

[0123] In a specific implementation, the extension direction of the convex rib TU2 may be the length direction of the heat exchanger 100, that is, the convex rib TU2 in the figure extends from the left side to the right side or from the right side to the left side, and the convex rib TU2 may extend along a straight line, a curve, or a broken line, etc., which is not limited in the present invention. The convex rib TU2 may also be a symmetrical structure with respect to the center line of the width direction of the heat exchanger 100, or the convex rib TU2 may be arranged obliquely with respect to the center line of the width direction of the heat exchanger 100.

[0124] In some embodiments, in the same type of inter-plate channel S0, there is a flow gap between the convex rib TU2 and the end area 106 away from the bypass flow channel BS; the middle area 105 includes a first sub-area AE3 and a second sub-area AE4, and the first sub-area AE3 and the second sub-area AE4 are arranged along the width direction of the heat exchanger 100. Along the width direction of the heat exchanger 100, part of the convex rib TU2 is located between the first sub-area AE3 and the second sub-area AE4, and the inter-plate channel S0 located in the first sub-area AE3 and the inter-plate channel S0 located in the second sub-area AE4 are connected through the flow gap S3 and the bypass flow channel BS.

[0125] Combination Figures 12 to 21As shown, in the inter-plate channel S0, the rib TU2 is located on one of the plates 5, and the rib TU2 is welded and sealed with another adjacent plate 5, so that within the length area where the rib TU2 extends, the fluids in the areas on both sides of the width direction of the rib TU2 do not interact, that is, within the length area where the rib TU2 extends, the fluids in the first sub-area AE3 and the second sub-area AE4 do not interact, which is convenient for distributing the fluid through the rib TU2. Compared with not setting the rib TU2, the fluid is easy to flow into the heat exchanger 100 from the inlet and directly flow out from the outlet through fewer paths, which is not conducive to the flow to the plate surface area of ​​the entire heat exchanger 100. Further, in the embodiment of the present invention, by reasonably setting the length of the rib TU2, the heat exchanger has a flow gap S3, which is convenient for realizing the fluid interaction between the first sub-area AE3 and the second sub-area AE4. In the embodiment of the present invention, one plate 5 is provided with one rib TU2, and in other embodiments, one plate can be provided with at least two ribs TU2, and the connection ends of adjacent ribs TU2 and the base plate are located on different sides of the length direction of the plate 5.

[0126] Optionally, the extension length of the rib TU2 can be greater than or equal to 1 / 3 or 1 / 4 of the length of the main body of the heat exchanger 100, and the present invention does not limit this. Specifically, when the flow cross-sectional area of ​​the bypass flow channel BS is large, the "attraction" effect on the fluid is strong, and the extension length of the rib TU2 can be set to be smaller. When the flow cross-sectional area of ​​the bypass flow channel BS is small, the extension length of the rib TU2 can be set to be longer to prevent the flow path of the fluid in the length direction of the heat exchanger from being smaller. By setting the rib TU2, when the fluid flows in the inter-plate channel S0, the fluid path is a U-shaped path.

[0127] Due to the setting of the convex rib TU2 structure, such as Figure 4 As shown, in some embodiments, the rib TU2 extends from the edge of one end region 106 in the length direction of the plate 5 to the other end region 106, and the bypass flow channel BS includes a first flow channel S4, and the first flow channel S4 includes at least two parts, along the width direction of the heat exchanger 100, at least one part is located on one side of the rib TU2, and at least one part is located on the other side of the rib TU2. Through the above arrangement, it is convenient to increase the structural strength of the plate 5. At this time, the extension distance of the first flow channel S4 along the width direction of the heat exchanger 100 is the sum of the extension distances of at least two parts.

[0128] Or Figure 3 As shown, in other embodiments, the bypass flow channel BS extends the entire width of the heat exchanger 100 , and the rib TU2 extends from the edge of the wall defining the bypass flow channel BS to the other end region 106 .

[0129] The structure of the plate 5 forming the first inter-plate channel S1 and the second inter-plate channel S2 is introduced below. In some embodiments, the plate 5 includes the first plate 1 and the second plate 2, based on which, the convex rib TU2 includes the first rib portion 14 and the second rib portion 22, the substrate of the plate 5 includes the first substrate 35 and the second substrate 36, the bypass channel BS includes the first bypass channel BS1 and the second bypass channel BS2, and the convex structure TU1 includes the first convex portion 11 and the second convex portion 201. Along the height direction of the heat exchanger 100, the first plate 1 and the second plate 2 are alternately stacked; the first plate 1 includes a first rib 14, a first substrate 35, a first convex portion 11, a first bypass structure BS1 and a first flow portion LT1, the first rib 14 extends along the length direction of the first plate 1, the first rib 14 protrudes toward the second plate 2 relative to the first substrate 35, the protruding direction of the first rib 14, the protruding direction of the first bypass structure BS1 and the first convex portion 11 are consistent, along the protruding direction away from the first rib 14, the first bypass structure BS1 has a first bypass groove BS3, the wall of the first bypass groove BS3 defines a first bypass channel S7, one end of the first rib 14 is connected to one end of the first plate 1 or to the first bypass structure BS1, the first flow portion LT1 is located between the other end of the first rib 14 and the other end of the first plate 1, and along the height direction of the heat exchanger 100, there is a gap between the first flow portion LT1 and the second plate 2.

[0130] And / or, in some embodiments, the second plate 2 includes a second rib 22, a second substrate 36, a second protrusion 201, a second bypass structure BS2 and a second flow portion LT2, the second rib 22 extends along the length direction of the second plate 2, the second rib 22 protrudes toward the first plate 1 relative to the second substrate 36, the second bypass structure BS2 has a second bypass groove BS4, the wall of the second bypass groove BS4 defines a second bypass channel S8, the protruding direction of the second rib 22, the protruding direction of the second bypass structure BS2 and the second protrusion 201 are consistent, one end of the second rib 22 and one end of the second plate 2 are connected to the second bypass structure BS2, the second flow portion LT2 is located between the other end of the second rib 22 and the other end of the second plate 2, and along the height direction of the heat exchanger 100, there is a gap between the second flow portion LT2 and the first plate 1.

[0131] In the embodiment of the present invention, the first plate 1 includes a first rib 14, and the second plate 2 includes a second rib 22. When projected along the height direction of the heat exchanger 100, the first rib 14 and the second rib 22 are staggered. Through the above arrangement, when the first plate 1 and the second plate 2 are alternately stacked, the first rib 14 and the second rib 22 can both play a guiding role for the fluid. In this article, the first plate 1 and the second plate 2 are alternately stacked, which can be a first plate 1 and a second plate 2 alternately stacked, or at least two first plates 1 and a second plate 2 are alternately stacked, or at least two first plates 1 and at least two second plates 2 are alternately stacked, or a first plate 1 and at least two second plates 2 are alternately stacked.

[0132] In summary, according to the heat exchanger 100 provided by the embodiment of the present invention, at least one sub-channel S01 has a bypass flow channel BS, and the bypass flow channel BS is located in the end area 106, so that when the fluid flows through at least one sub-channel S01, the fluid can be better distributed under the action of the bypass channel BS, thereby increasing the flow area of ​​the fluid in the heat exchanger 100 and increasing the heat exchange area of ​​the heat exchanger 100.

[0133] Furthermore, combined with Figures 17 to 21 As shown, in an embodiment of the present invention, the heat exchanger 100 has an intermediate area 105, and the heat exchanger 100 includes at least two plates 5, and the plates 5 are stacked along the height direction of the heat exchanger 100. The plates 5 include a plurality of protruding structures TU1, and at least a part of the protruding structures TU1 are scattered in the intermediate area 105. The protruding structures TU1 located in the intermediate area 105 are arranged in an array along a first direction E and a second direction F, and the first direction E intersects with the second direction F. Since the path of the heat exchanger 100 in the length direction is relatively large, in order to reduce the flow resistance of the fluid, one of the angles between the first direction E and the second direction F is defined as angle α, α is toward the length direction of the heat exchanger 100, and α is less than 90 degrees. At this time, α is an acute angle structure. By providing a plurality of raised structures TU1 arranged in an array along the first direction E and the second direction F on the plate 5, it is convenient to distribute the fluid, and by setting the angle α between the first direction E and the second direction F toward the length direction of the heat exchanger 100 to be less than 90 degrees, at this time, along the length direction of the heat exchanger 100, the angle between the first direction E and the second direction F is small, so that the fluid has a smaller flow resistance when flowing along the length direction of the heat exchanger 100, which facilitates increasing the flow path of the fluid in the length direction of the heat exchanger 100.

[0134] To further reduce the flow resistance in the length direction of the heat exchanger 100 , in some embodiments, α1 is greater than or equal to 15 degrees and less than or equal to 75 degrees.

[0135] In order to increase the flow area of ​​the fluid in the heat exchanger 100, in some embodiments, the heat exchanger 100 further has an end area 106, along the length direction of the heat exchanger 100, one end area 106 is located on one side of the middle area 105, and the other end area 106 is located on the other side of the middle area 105; a part of the convex structures TU1 are scattered in at least one end area 106, and the convex structures TU1 located in the end area 106 are arranged in an array along the first direction E and the second direction F. By providing the convex structures TU1 in the end area 106, it is convenient to guide and distribute the fluid, so as to increase the flow area of ​​the fluid in the plate 5.

[0136] In the embodiment of the present invention, the end area 106 includes a first area AE1 and a second area AE2, the middle area 105 is located between the first area AE1 and the second area AE2, a part of the protruding structures TU1 are dispersed in the first area AE1, and a part of the protruding structures TU1 are dispersed in the second area AE2, the structural graphics of the protruding structures TU1 located in the first area AE1 and the second area AE2 are the same or similar, and the protruding structure TU1 located in the end area 106 is the same or similar to the protruding structure TU1 located in the middle area 105.

[0137] In some embodiments, another angle between the first direction E and the second direction F is defined as α2, α2 is oriented toward the width direction of the heat exchanger 100, and α2 is greater than 90 degrees. At this time, the angle α2 is an obtuse angle, for example, α2 can be greater than or equal to 105 degrees and less than or equal to 165 degrees. Through the above arrangement, it is convenient to distribute the fluid through the obtuse angle structure, and it is convenient to guide the fluid to flow to the position of the flange 4.

[0138] In the embodiment of the present invention, if the angle of α is set too small, the angle of α2 will be increased, and the area where the fluid is introduced into the flange 4 will be smaller. If the angle of α2 is set too small, the angle of α1 will be increased, and the flow resistance along the length direction of the heat exchanger 100 will be increased. Optionally, the angle of α can be greater than or equal to 15 degrees and less than or equal to 75 degrees, and α2 can be greater than or equal to 105 degrees and less than or equal to 165 degrees. Through the above settings, it is convenient to improve the fluid distribution at the bend of the rib TU2 and guide the fluid to flow to the flange 4.

[0139] Based on this, the convex rib TU2 may include a fold line structure with arc transitions between adjacent fold lines. Among the adjacent fold lines, the straight line where one fold line is located is parallel to the first direction E, and the straight line where the other fold line is located is parallel to the second direction F. At this time, a first angle may be formed between the adjacent fold lines, and the first angle is toward the width direction of the heat exchanger. The first angle may be an obtuse angle.

[0140] In some embodiments, the plate 5 includes a first plate 1, and the first plate 1 includes a first substrate 35 and a first convex portion 11 connected to each other. In this article, the first substrate 35 and the first convex portion 11 are an integral stamping part, and the main body of the first substrate 35 is a flat plate structure. On one side of the thickness direction of the first plate 1, the first convex portion 11 protrudes from the first substrate 35 to the direction away from the first substrate 35, and on the other side of the thickness direction of the first plate 1, a concave portion is formed corresponding to the position where the first convex portion 11 is located. The first convex portion 11 has a first edge B1 and a second edge B2. Along the length direction of the heat exchanger 100, the angle α3 between the first edge B1 and the second edge B2 is less than 90 degrees. At this time, the first convex portion 11 can be a rhombus-like structure. And / or in the first reference quadrilateral D1 formed by connecting the center points of four adjacent first convex portions 11, along the length direction of the heat exchanger 100, one of the angles α4 of the first reference quadrilateral D1 is less than 90 degrees. In this article, the thickness direction of the plate 5 is parallel to or coincides with the height direction of the heat exchanger 100. In the embodiment of the present invention, the angles α4 and α3 are equal.

[0141] Further, in some embodiments, the first convex portion 11 has a third edge B3 and a fourth edge B4, and along the length direction toward the heat exchanger 100, the angle α31 between the third edge B3 and the fourth edge B4 is less than 90 degrees, and / or in the first reference quadrilateral D1 formed by the center point connection line of four adjacent first convex portions 11, along the length direction toward the heat exchanger 100, another angle α41 of the first reference quadrilateral D1 is less than 90 degrees. In the embodiment of the present invention, the angles of α41 and α31 can be equal, the angles of α41 and α4 can be equal, and the angles of α31 and α3 can be equal. The extension direction of the first edge B1 and the extension direction of the third edge B3 can be parallel or substantially parallel to the first direction E, and the extension direction of the second edge B2 and the extension direction of the fourth edge B4 can be parallel or substantially parallel to the second direction F. The two directions being substantially parallel means that the acute angle defined by the two directions is less than or equal to 10 degrees, or is defined according to the needs of the user.

[0142] Along the width direction toward the heat exchanger 100, the angle α5 between the first edge B1 and the fourth edge B4 is greater than 90 degrees, and / or in the first reference quadrilateral D1 formed by connecting the center points of four adjacent first protrusions 11, along the width direction toward the heat exchanger 100, another angle α6 of the first reference quadrilateral D1 is greater than 90 degrees.

[0143] In some embodiments, the heat exchanger 100 further has an end area 106, and a portion of the protruding structures TU1 are distributed in at least one end area 106. In the first plate 1, at least a portion of the protruding structures TU1 located in the end area 106 are the same or similar patterns as the protruding structures TU1 located in the middle area 105.

[0144] Alternatively, for the raised structure TU1 located in the end area 106, in the second reference quadrilateral D2 formed by connecting the center points of four adjacent first protrusions 11, along the length direction of the heat exchanger 100, the angle α7 of the second reference quadrilateral D2 is less than 90 degrees, and along the width direction of the heat exchanger 100, the angle α8 of the second reference quadrilateral D2 is greater than 90 degrees.

[0145] In some embodiments, the plate 5 further includes a second plate 2, the first plate 1 and the second plate 2 are alternately stacked along the height direction of the heat exchanger 100, the heat exchange region has an inter-plate channel S0, and the inter-plate channel S0 is located between the first plate 1 and the second plate 2. The second plate 2 includes a second base plate 36 and a second protrusion 201 connected to each other, the second protrusion 201 protrudes from the second base plate 36 away from the second base plate 36, and in the second reference quadrilateral D2 formed by connecting the center points of four adjacent second protrusions 201, along the length direction of the heat exchanger 100, the angle α9 of the third reference quadrilateral D3 is less than 90 degrees, and along the width direction of the heat exchanger 100, the angle α10 of the third reference quadrilateral D3 is greater than 90 degrees.

[0146] Furthermore, in some embodiments, Fig.21 As shown, the second plate 2 further includes a low section DW, and on the same side of the thickness direction of the second plate 2, the low section DW is recessed relative to the second convex portion 201, and the low section DW is flush with the second substrate 36 or the low section DW is recessed from the second substrate 36 in a direction away from the second convex portion 201. The low sections DW are arranged in an array along the first direction E and the second direction F, and along the length direction and the width direction of the second plate 2, the low sections DW and the second convex portion 201 are arranged alternately; in the fourth reference quadrilateral D4 formed by the center point connection line of four adjacent low sections DW, along the length direction of the heat exchanger 100, the included angle α11 of the fourth reference quadrilateral D4 is less than 90 degrees, and along the width direction of the heat exchanger 100, the included angle α12 of the fourth reference quadrilateral D4 is greater than 90 degrees.

[0147] In some embodiments, the heat exchanger 100 further has an end area 106, and a partial number of the protruding structures TU1 are distributed in at least one end area 106. In the second plate 2, the protruding structure TU1 located in the end area 106 and the protruding structure TU1 located in the middle area 105 are the same or similar patterns; or the protruding structure TU1 located in the end area 106 is a diamond-like structure.

[0148] For example, the raised structure TU1 of the first plate 1 is defined as the first protrusion 11, and the raised structure TU2 of the second plate 2 is defined as the second protrusion 201. A part of the first protrusions 11 may have the same or similar structure as the second protrusions 201, and a part of the second protrusions 201 may have a similar structure to the first protrusions 11.

[0149] In summary, according to the heat exchanger provided by the embodiment of the present invention, a plurality of protrusion structures TU1 arranged in an array along the first direction E and the second direction F are provided on the plate 5, so as to facilitate the distribution of the fluid, and by setting the angle α between the first direction X and the second direction Y toward the length direction of the heat exchanger to be less than 90 degrees, at this time, along the length direction of the heat exchanger, the angle between the first direction and the second direction is small, so that the fluid has a smaller flow resistance when flowing along the length direction of the heat exchanger, which facilitates increasing the flow path of the fluid in the length direction of the heat exchanger.

[0150] like Figure 22-Figure 26 As shown, the heat exchanger includes a first plate 1 and a second plate 2 , and a portion of the heat exchanger may be formed by alternately stacking the first plate 1 and the second plate 2 .

[0151] There is a first inter-plate channel between the first plate 1 and the second plate 2, the first plate 1 includes a plurality of first protrusions and a first substrate 35, the first protrusion protrudes relative to the first substrate 35 toward the second plate 2; the first plate 1 includes a first rib 14, the first rib 14 protrudes relative to the first substrate 35 toward the second plate 2, and the protrusion direction of the first rib 14 is consistent with the protrusion direction of the first protrusion; the plurality of first protrusions include a first group of first protrusions K1 and a second group of first protrusions K2, the first group of first protrusions K1 and the second group of first protrusions K2 are both composed of first protrusions adjacent to the first rib 14; the direction perpendicular to the extension direction of the first rib 14 is defined as a third direction, along the third direction, the first group of first protrusions K1 are located on one side of the first rib 14, the second group of first protrusions K2 are located on the other side of the first rib 14, and along the third direction, the first group of first protrusions K1 are closer to the first rib 14 than the second group of first protrusions K2. The third direction is indicated by W in the figure. In this embodiment, the first plate 1 is rectangular as a whole, and the extension direction of the first rib 14 is basically the same as the extension direction of the first rib 14. In other embodiments, the extension direction of the first rib 14 may also be basically the same as the width direction of the first plate 1.

[0152] like Fig. 22 , Fig.25 As shown, along the third direction, the first group of first protrusions K1 is closer to the first rib 14 than the second group of first protrusions K2, so that the flow resistance of the channel formed between the first group of first protrusions K1 and the first rib 14 can be smaller than the flow resistance of the channel formed between the second group of first protrusions K2 and the first rib 14, so that the bypass flow formed between the first group of first protrusions K1 and the first rib 14 is relatively reduced, so that more fluid flows to the channel between the first protrusions 11, thereby improving the heat exchange performance of the heat exchanger. The black unidirectional arrows in Figures A and B show the flow path of the fluid between the first protrusion 11 and the first rib 14. It should be noted that Figure A only shows a part of the first group of first protrusions K1 and a part of the second group of first protrusions K2.

[0153] The heat exchanger includes a first channel 101 and a second channel 102. Along the third direction, the first channel 101 and the second channel 102 are located on both sides of the first rib 14. Along the direction parallel to the first substrate 35, one end of the first rib 14 is connected to the first end 51 of the first plate 1, and the other end of the first rib 14 is not connected to the second end 52 of the first plate 1. The first channel 101 and the second channel 102 are both connected to the first inter-plate channel, so that the fluid can flow in a U-shaped path around the first rib 14, so that the fluid has at least two flow sections. In this embodiment, the first channel 101 is used to introduce the fluid into the first inter-plate channel, and the second channel 102 is used to export the fluid from the first inter-plate channel, or in other words, the first channel 101 is the inlet channel of the fluid, and the second channel 102 is the outlet channel of the fluid. Along the third direction, the first group of first protrusions K1 and the first channel 101 are located on the same side of the first rib 14, and the second group of first protrusions K2 and the second channel 102 are located on the same side of the first rib 14. In this way, the fluid flow on the upstream side of the first inter-plate channel is more evenly distributed in the third direction, which is beneficial to improving the heat exchange performance of the heat exchanger.

[0154] In the direction perpendicular to the first substrate 35, the orthographic projection of the top end 225 of the second rib 22 on the first substrate 35 is located between the second group of first protrusions K2 and the first rib 14. Since the space between the second group of first protrusions K2 and the first rib 14 is relatively large, the welding area between the top end 225 of the second rib 22 and the first substrate 35 of another adjacent first plate 1 (not shown in the figure) is larger, thereby improving the firmness and sealing of the welding here.

[0155] The number of the first protrusions 11 in the first group of first protrusions K1 is more than two, and the first protrusions 11 in the first group of first protrusions K1 are arranged along the extension direction of the first rib 14. In this way, along the extension direction of the first rib 14, the bypass flow between the first protrusion 11 and the first rib 14 can be continuously reduced, thereby improving the heat exchange performance of the heat exchanger.

[0156] In this embodiment, along the third direction, the width of the first group of first protrusions K1 is greater than the width of the second group of first protrusions K2. The relatively wide first group of first protrusions K1 has a stronger fluid resistance, which can further reduce the fluid flow between the first group of first protrusions K1 and the first rib 14. In addition, in order to adapt to different heat exchange requirements, the width of the first plate 1 will have different widths according to design requirements. If the widths of all first protrusions 11 on the first plate 1 are the same, the first protrusions 11 may not be fully arranged in the third direction, resulting in a large gap between the first protrusions 11 and the first rib 14. In this embodiment, the width of the second group of first protrusions K2 can be the same as the width of the normal first protrusions 11. By increasing the width of the first group of first protrusions K1, the aforementioned gap is reduced, and then without changing the width of the normal first protrusion 11, the width of the first plate 1 can be adjusted within a smaller range (i.e., within the width of a normal first protrusion 11).

[0157] like Fig. 22 , Fig.26 As shown, the end of the first rib 14 relatively close to the second end 52 of the first plate 1 is defined as the open end 142, and along the extension direction of the first rib 14, the second group of first protrusions K2 extends to the vicinity of the open end 142. On the one hand, since the fluid makes a sharp turn near the open end 142, the fluid is easily thrown away from the open end 142 near the open end 142; on the other hand, the distance between the second group of first protrusions K2 and the first rib 14 is relatively large, and the flow resistance of the channel between the second group of first protrusions K2 and the first rib 14 is relatively small, which makes it easier for the fluid to enter between the second group of first protrusions K2 and the first rib 14 from the vicinity of the open end 142. The above two effects are superimposed, which can make the flow near the open end 142 in a relatively moderate range.

[0158] like Fig.23 , Fig.26 , Fig. 27 As shown, along the extension direction of the first rib 14, the other end of the second group of first protrusions K2 is basically flush with one end of the second rib 22 of the second plate 2, which can adapt to the structure of the second rib 22 of the second plate 2 and facilitate strengthening the welding between the second rib 22 of the second plate 2 and the first plate 1. Fig. 27 FIG. 2 shows an orthographic projection 22L of the top 225 of the second rib 22 on the first plate 1 . The top 225 of the second rib 22 can be welded to another adjacent first plate 1 .

[0159] Specifically, Fig.26 , Fig. 27As shown, the plurality of first protrusions include a third group of first protrusions K3. Along the third direction, the third group of first protrusions K3 and the second group of second protrusions K2 are located on the same side of the first rib 14. The first protrusions 11 in the third group of first protrusions K3 are all adjacent to the first rib 14. The first protrusions 11 in the third group of first protrusions K3 extend along the extension direction of the first rib 14. Along the extension direction of the first rib 14, the third group of first protrusions K3 are basically located between the orthographic projection of the second rib 22 of the first plate 1 and the first end 51 of the first plate 1. The distance between the third group of first protrusions K3 and the first rib 14 is defined as S1, and the distance between the first group of first protrusions K1 and the first rib 14 is defined as S2. S1 is the same or substantially the same as S2. It should be noted that, Fig.26 Only a portion of the first group of first protrusions K1 , a portion of the second group of first protrusions K2 , and a portion of the third group of first protrusions K3 are shown.

[0160] In this embodiment, the edge of the first protrusion 11 is rhombus-shaped. In other embodiments, the edge of the first protrusion 11 may be triangular or hexagonal.

[0161] like Figure 28-Figure 47 The figure shows a first embodiment of the heat exchanger 100, the heat exchanger 100 comprises a plurality of plates 5, the plurality of plates 5 are stacked, a first inter-plate channel S1 is provided between the plate 5 and the plate 5 on one side adjacent to each other, a second inter-plate channel S2 is provided between the plate 5 and the plate 5 on the other side adjacent to each other, the first inter-plate channel S1 and the second inter-plate channel S2 are alternately provided, the first inter-plate channel S1 and the second inter-plate channel S2 are not connected, the first inter-plate channel S1 is for the flow of the first fluid, the second inter-plate channel S2 is for the flow of the second fluid, and the first fluid and the second fluid perform heat exchange. The first inter-plate channel S1 and the second inter-plate channel S2 are alternately provided, so that the area for heat exchange between the first fluid and the second fluid is large, and the heat exchange effect of the heat exchanger 100 is relatively good. In other embodiments, there may be a first inter-plate channel S1 between the plate 5 and the adjacent plate 5 on one side, and there may also be a first inter-plate channel S1 between the plate 5 and the adjacent plate 5 on the other side, and there may be a second inter-plate channel S2 between the next layer of plates 5, that is, two layers of first inter-plate channels S1 are continuously arranged, and then one layer of second inter-plate channel S2 is arranged, so that heat exchange between the first fluid and the second fluid can be achieved. In this embodiment, the second fluid refers to the coolant, which is mainly a coolant, such as cooling water or cooling oil, and the first fluid refers to the refrigerant, which is mainly a refrigerant, such as R134a, R1234yf, etc. Fig.31, multiple plates 5 are stacked, and there is a first inter-plate channel S1 or a second inter-plate channel S2 between the plates 5 and the adjacent plates 5. In other embodiments, two or more layers of the second inter-plate channel S2 are continuously arranged, and then several layers of the first inter-plate channel S1 are arranged. The rib TU2 abuts against the adjacent plates 5, and the connecting portion LT0 connects the areas on both sides of the rib TU2. The connecting portions LT0 on both sides of the plates 5 at least partially overlap, and at least two layers of coolant are arranged in the middle to reduce the heat exchange temperature difference on both sides of the plates 5, thereby reducing the occurrence of thermal bridges. For the convenience of description, the upper and lower directions are defined as the upper and lower directions in the attached drawings of the specification. Fig.28 The upper and lower directions of the heat exchanger 100 are defined as the upper and lower directions of the heat exchanger 100, and the upper and lower directions only represent relative positions; the height direction, length direction, and width direction of the heat exchanger 100 are defined as the height direction, length direction, and width direction of the heat exchanger 100 in the attached drawings of the specification. Fig.28 In the height direction, length direction, and width direction of the heat exchanger 100, in this application, the height direction of the heat exchanger 100 is consistent with the stacking direction of the plate 5; in this application, the length direction of the plate 5 is consistent with the length direction of the heat exchanger 100, and the width direction of the plate 5 is consistent with the width direction of the heat exchanger 100. In this application, the directions of adjacent sides are consistent, the directions of adjacent sides are consistent, the adjacent side refers to the adjacent side facing upward, and the adjacent other side refers to the adjacent side facing downward; or, the adjacent side refers to the adjacent side facing downward, and the adjacent other side refers to the adjacent side facing upward.

[0162] This article focuses on improving the structure of the plate 5 of the heat exchanger, which is described in detail below with reference to the accompanying drawings.

[0163] like Figure 28-Figure 34 In the embodiment, the heat exchanger 100 includes a plate 5, and the plate 5 includes a rib TU2. The rib TU2 is protruding from the plate 5, and the rib TU2 and the plate 5 are an integral structure. For example, the plate 5 is punched to form the rib TU2, and the rib TU2 is located in the first inter-plate channel S1 and the second inter-plate channel S2. Along the height direction of the plate, the rib TU2 abuts against the adjacent plates 5. Along the length direction of the plate 5, the rib TU2 extends from one side of the plate 5 to the other opposite side. The rib TU2 divides the plate 5 into two parts along the width direction of the plate 5. Along the extension direction of the rib TU2, the rib TU2 and the side of the plate 5 are connected. There is a connecting portion LT0 between them, and the connecting portion LT0 connects the areas on both sides of the rib TU2. Along the direction perpendicular to the plate 5, the connecting portion LT0 in the first inter-plate channel S1 and the connecting portion LT0 in the adjacent second inter-plate channel S2 at least partially overlap. When the first fluid and the second fluid flow from one side of the rib TU2 to the other side along the width direction of the plate 5, since the connecting portion LT0 in the first inter-plate channel S1 and the connecting portion LT0 in the second inter-plate channel S2 at least partially overlap, the first fluid and the second fluid at least partially overlap in the flow area, which increases the heat exchange area of ​​the first fluid and the second fluid, thereby enhancing the heat exchange effect.

[0164] Combination Figure 32-Figure 33 In this embodiment, along the length direction of the plate 5, the extension length of the rib TU2 is greater than half of the length of the plate 5, the rib TU2 in the first inter-plate channel S1 and the rib TU2 in the adjacent second inter-plate channel S2 extend from the same side of the plate 5 to the other opposite side, the connecting portion LT0 in the first inter-plate channel S1 and the connecting portion LT0 in the adjacent second inter-plate channel S2 are located on the same side of the plate 5, the overlapping area of ​​the connecting portion LT0 in the first inter-plate channel S1 and the connecting portion LT0 in the adjacent second inter-plate channel S2 is increased, the heat exchange area between the first fluid and the second fluid is further increased, and the heat exchange effect is enhanced.

[0165] Combination Fig.34 In other embodiments, the rib TU2 in the first inter-plate channel S1 and the rib TU2 in the adjacent second inter-plate channel S2 can extend from different sides of the plate 5 to the other opposite side, and the extension length of the rib TU2 is less than half the length of the plate 5. The connecting portion LT0 in the first inter-plate channel S1 and the connecting portion LT0 in the adjacent second inter-plate channel S2 overlap near the center line along the length direction of the plate 5, thereby increasing the heat exchange area between the first fluid and the second fluid, thereby enhancing the heat exchange effect.

[0166] Combination Fig.35 In this embodiment, along the direction perpendicular to the plate 5, the rib TU2 in the first inter-plate channel S1 and the rib TU2 in the adjacent second inter-plate channel S2 are staggered. Along the direction perpendicular to the plate 5, the rib TU2 is protruded relative to the plate 5 toward the side close to the adjacent plate 5, and the rib TU2 abuts against the adjacent plate 5. After the rib TU2 abuts against the adjacent plate 5, the first inter-plate channel S1 and the second inter-plate channel S2 are separated into two parts, and the connection strength between the adjacent plates 5 is increased. In addition, the stamping distance of the rib TU2 is small, the wall thickness of the rib TU2 is less thinned, and the strength of the rib TU2 is enhanced.

[0167] Combination Fig.36 In other embodiments, the rib TU2 in the first inter-board channel S1 and the rib TU2 in the adjacent second inter-board channel S2 can also be arranged to overlap along the direction perpendicular to the plate 5. The overlap here means that the orthographic projections of the rib TU2 in the first inter-board channel S1 and the rib TU2 in the adjacent second inter-board channel S2 overlap on the plate 5, and the rib TU2 forms a corresponding groove CB on the other side of the plate 5. The rib TU2 protrudes to the groove CB of the adjacent plate 5 and abuts against the groove CB. After the groove CB and the rib TU2 abut, the first inter-board channel S1 and the second inter-board channel S2 are separated into two parts, and the connection strength between the adjacent plates 5 is increased.

[0168] Combination Fig.29 , Fig.32 , Fig.33 , Fig.37 In this embodiment, the heat exchanger 100 includes a first channel 101, a second channel 102, a third channel 103 and a fourth channel 104. Along the length direction of the plate 5, the first channel 101, the second channel 102, the third channel 103 and the fourth channel 104 are all arranged close to the end of the plate 5 opposite to the connecting portion LT0.

[0169] Combination Fig.29 , Fig.32 , Fig.33 , Fig.37In this embodiment, the plate 5 includes four corner holes 53, and the four corner holes 53 are all arranged near the end of the plate 5 opposite to the connecting portion LT0. The plates 5 are stacked, and the four corner holes of each plate 5 are respectively aligned along the stacking direction of the plates 5. The four corner holes are respectively aligned along the stacking direction of the plates 5 to form four channels, namely the first channel 101, the second channel 102, the third channel 103 and the fourth channel 104. The first channel 101 is for the refrigerant to flow into the heat exchanger 100, and the second channel 102 is for the refrigerant to flow out of the heat exchanger 100. At the first channel 101 and the second channel 102, the first inter-plate channel S1 is opened, and the first channel 101 and the second channel 102 are connected through the first inter-plate channel S1. At the first channel 101 and the second channel 102, the second inter-plate channel S2 is not opened, and the first channel 101 and the second channel 102 are not connected to the second inter-plate channel S2. In this embodiment, the third hole 103 is for the coolant to flow into the heat exchanger 100, and the fourth hole 104 is for the coolant to flow out of the heat exchanger 100. At the third hole 103 and the fourth hole 104, the second inter-plate channel S2 is open, and the third hole 103 and the fourth hole 104 are connected through the second inter-plate channel S2. At the third hole 103 and the fourth hole 104, the first inter-plate channel S1 is not open, and the third hole 103 and the fourth hole 104 are not connected to the first inter-plate channel S1. The refrigerant flows in the first inter-plate channel S1, and the coolant flows in the second inter-plate channel S2, and the refrigerant and the coolant exchange heat. In this embodiment, along the width direction of the plate 5, the first hole 101 and the fourth hole 104 are located on one side of the rib TU2, and the third hole 103 and the second hole 102 are located on the other side of the rib TU2. In this embodiment, the rib TU2 divides the plate 5 into a first side 15 and a second side 16, the first channel 101 is the inflow channel of the refrigerant, and the second channel 102 is the outflow channel of the refrigerant. The refrigerant flows into the heat exchanger 100 from the first channel 101, first flows on the first side 15 of the plate 5, then flows around the rib TU2 to the second side 16 of the plate 5, and flows out of the heat exchanger 100 from the second channel 102. The setting of the rib TU2 allows the refrigerant to flow in a U-shaped line around the rib TU2, so that the refrigerant has two flow sections, which can increase the flow path of the refrigerant, increase the heat exchange area between the refrigerant and the coolant, and improve the effect of the heat exchanger 100. In this embodiment, the third channel 103 is the inlet channel of the coolant, and the fourth channel 104 is the outlet channel of the coolant. The coolant flows into the heat exchanger 100 from the third channel 103, first flows on the second side 16 of the plate 5, then flows around the rib TU2 to the first side 15 of the second plate 2, and flows out of the heat exchanger 100 from the fourth channel 104. The coolant flows in a U-shaped line around the rib TU2. The setting of the rib TU2 can make the coolant have two flow sections, which can increase the flow path of the coolant and improve the heat exchange effect between the coolant and the refrigerant.And along the width direction of the plate 5, the inflow of the refrigerant and the outflow of the coolant are located on one side of the rib TU2, and the outflow of the refrigerant and the inflow of the coolant are located on the other side of the rib TU2. The refrigerant and the coolant always maintain countercurrent in the flow path, thereby increasing the heat exchange temperature difference between the refrigerant and the coolant and enhancing the heat exchange performance.

[0170] Combination Fig.38 and Fig.39 In other embodiments, the first channel 101 and the fourth channel 104 can be distributed along the length direction of the plate 5, so that the overlapping area of ​​the refrigerant and the coolant flowing at the first side 15 is increased, thereby increasing the heat exchange area between the refrigerant and the coolant, thereby improving the heat exchange effect. Fig.40 and Fig.41 In other embodiments, the second channel 102 and the third channel 103 can be distributed along the length direction of the plate 5, and the overlapping area of ​​the refrigerant and the coolant flowing at the second side 16 is increased, thereby increasing the heat exchange area of ​​the refrigerant and the coolant, and thus improving the heat exchange effect. The first channel 101 is the inlet channel of the refrigerant, and the second channel 102 is the outlet channel of the refrigerant. The refrigerant flows into the heat exchanger 100 from the first channel 101, first flows on the first side 15 of the plate 5, then flows around the rib TU2 to the second side 16 of the plate 5, and flows out of the heat exchanger 100 from the second channel 102. The setting of the rib TU2 allows the refrigerant to flow in a U-shaped line around the rib TU2, so that the refrigerant has two flow sections, which can increase the flow path of the refrigerant, increase the heat exchange area of ​​the refrigerant and the coolant, and improve the effect of the heat exchanger 100. In this embodiment, the third channel 103 is the inflow channel of the coolant, and the fourth channel 104 is the outflow channel of the coolant. The coolant flows into the heat exchanger 100 from the third channel 103, first flows on the second side 16 of the plate 5, then flows around the second rib 22 to the first side 15 of the second plate 2, and flows out of the heat exchanger 100 from the fourth channel 104. The coolant flows around the rib TU2 in a U-shaped line. The setting of the rib TU2 can make the coolant have two flow sections, which can increase the flow path of the coolant and improve the heat exchange effect of the coolant and the refrigerant. In addition, along the width direction of the plate 5, the inflow of the refrigerant and the outflow of the coolant are located on one side of the rib TU2, and the outflow of the refrigerant and the inflow of the coolant are located on the other side of the rib TU2. The refrigerant and the coolant always maintain countercurrent on the flow path, and the heat exchange temperature difference between the refrigerant and the coolant is increased, thereby enhancing the heat exchange performance.

[0171] Combination Fig.37In this embodiment, along the width direction of the plate 5, the fourth channel 104 is closer to the rib TU2 than the first channel 101, and the second channel 102 is closer to the rib TU2 than the third channel 103; or, the first channel 101 is closer to the rib TU2 than the fourth channel 104, and the third channel 103 is closer to the rib TU2 than the second channel 102, the refrigerant flows in from the side close to the rib TU2 and flows out from the side away from the rib TU2, and the coolant flows in from the side away from the rib TU2 and flows out from the side close to the rib TU2, which reduces the probability of the refrigerant or the coolant accumulating in the area near the rib TU2, improves the fluid distribution rate, and thus increases the exchange effect.

[0172] Combination Figure 42-Figure 47 In other embodiments, along the width direction of the plate 5, the fourth channel 104 is closer to the rib TU2 than the first channel 101, and the third channel 103 is closer to the rib TU2 than the second channel 102; or, the first channel 101 is closer to the rib TU2 than the fourth channel 104, and the second channel 102 is closer to the rib TU2 than the third channel 103. The refrigerant and the coolant always maintain countercurrent on the flow path, and the overlapping area of ​​the refrigerant and the coolant flowing at the first side 15 or the second side 16 is increased, the heat exchange area of ​​the refrigerant and the coolant is increased, and the heat exchange effect is improved. The heat exchange temperature difference between the refrigerant and the coolant is increased, and the heat exchange performance is enhanced.

[0173] Combination Figure 48-Figure 73The heat exchanger 100 includes a plurality of plates 5, and the plurality of plates 5 are stacked. In this embodiment, a first inter-plate channel s1 is provided between the plate 5 and the plate 5 on one side, and a second inter-plate channel s2 is provided between the plate 5 and the plate 5 on the other side. The first inter-plate channel s1 and the second inter-plate channel s2 are alternately provided, and the first inter-plate channel s1 and the second inter-plate channel s2 are not connected. The first inter-plate channel s1 is provided for the flow of the first fluid, and the second inter-plate channel s2 is provided for the flow of the second fluid, and the first fluid and the second fluid are heat exchanged. The first inter-plate channel s1 and the second inter-plate channel s2 are alternately provided, so that the area for heat exchange between the first fluid and the second fluid is large, and the heat exchange effect of the heat exchanger 100 is relatively good. In other embodiments, there may be a first inter-plate channel s1 between the plate 5 and the plate 5 on the adjacent side, and there may also be a first inter-plate channel s1 between the plate 5 and the plate 5 on the adjacent other side, and there may be a second inter-plate channel s2 between the next layer of plates 5, that is, two layers of first inter-plate channels s1 are arranged continuously, and then one layer of second inter-plate channels s2 is arranged, so that heat exchange between the first fluid and the second fluid can be achieved. In other embodiments, two or more layers of second inter-plate channels s2 may be arranged continuously, and then several layers of first inter-plate channels s1 are arranged. In this embodiment, the second fluid refers to the coolant, which is mainly a coolant, such as cooling water or cooling oil. The first fluid in this application refers to the refrigerant, which is mainly a refrigerant, such as R134a, R1234yf, etc. For the convenience of description, the upper and lower directions are defined as those in the attached drawings of the specification. Fig.48 The upper and lower directions of the heat exchanger 100 are defined as the upper and lower directions of the heat exchanger 100, and the upper and lower directions only represent relative positions; the height direction, length direction, and width direction of the heat exchanger 100 are defined as the height direction, length direction, and width direction of the heat exchanger 100 in the attached drawings of the specification. Fig.48 In the height direction, length direction, and width direction of the heat exchanger 100, in this application, the height direction of the heat exchanger 100 is consistent with the stacking direction of the plate 5; in this application, the length direction of the plate 5 is consistent with the length direction of the heat exchanger 100, and the width direction of the plate 5 is consistent with the width direction of the heat exchanger 100. In this application, the directions of the adjacent sides are consistent, the directions of the adjacent sides are consistent, the adjacent side refers to the adjacent side facing upward, and the adjacent other side refers to the adjacent side facing downward; or, the adjacent side refers to the adjacent side facing downward, and the adjacent other side refers to the adjacent side facing upward.

[0174] In this embodiment, the plate 5 includes a first plate 1 and a second plate 2, the first plate 1 and the second plate 2 are alternately stacked, a first inter-plate channel s1 is provided between the first plate 1 and the second plate 2 on one side, a second inter-plate channel s2 is provided between the first plate 1 and the second plate 2 on the other side, and the first inter-plate channel s1 and the second inter-plate channel s2 are alternately provided. In this embodiment, the first plate 1 includes a plurality of first convex portions 11 and a first substrate 35, the first convex portion 11 protrudes toward the second plate 2 relative to the first substrate 35, and the first convex portion 11 has a second groove 122 on the side facing the second plate 2. The first convex portion 11 includes a first high-level segment 12 and a first low-level segment 13, along the vertical direction of the first substrate 35, the first high-level segment 12 is closer to the second plate 2 than the first low-level segment 13, the first high-level segment 12 is closer to the second substrate 36 of the second plate 2 than the first low-level segment 13, and the second groove 122 is located in the first low-level segment 13. The first substrate 35 refers to the first plate 1 before being punched, and the second substrate 36 refers to the second plate 2 before being punched.

[0175] In this embodiment, the second plate 2 includes a plurality of recesses 21, the recesses 21 protrude away from the first plate 1 relative to the first substrate 35 of the second plate 2, the second plate 2 includes the recesses 21, the recesses 21 include the grooves 211, and the recesses 21 have the grooves 211 on the side facing the first plate 1. In this embodiment, the second plate 2 includes the second substrate 36, the recesses 21 are recessed in the direction away from the first plate 1 relative to the second substrate 36, the recesses 21 are recessed in the direction away from the first substrate 35 relative to the second substrate 36, and along the height direction of the heat exchanger 100, the recesses 21 and the first high-level section 12 are staggered, and the staggered setting means that the projections of the first high-level section 12 and the recesses 21 on the plate surface of the first plate 1 do not overlap. The wall forming the first inter-plate channel s1 includes the first low-level section 13 and the second substrate 36, and the wall forming the first inter-plate channel s1 includes the first substrate 35 and the recesses 21. The first plate 1 and the second plate 2 are fixedly connected, the recess 21 and the first base plate 35 are opposite, and the recess 211 forms a part of the first inter-plate channel s1. The existence of the recess is conducive to strengthening the boiling heat transfer of the refrigerant. The setting of the first low-level section 13 is conducive to increasing the heat exchange area of ​​the refrigerant. The joint setting of the recess and the first low-level section 13 is conducive to improving the heat exchange effect of the heat exchanger. In this embodiment, the first plate 1 and the second plate 2 are welded and connected. After the plate exchange 5 is stacked, the whole is placed in a brazing furnace for brazing. The connection method of the first plate 1 and the second plate 2 is simple, and the molding process of the heat exchanger 100 is simple. In addition, fins are usually set between adjacent plates 5 to enhance the heat exchange area to improve the heat exchange effect. In this embodiment, no fins are set between adjacent plates 5. By setting point waves on the plates 5 to enhance the heat exchange area, good heat exchange performance is achieved. Compared with the scheme of setting fins, fins are saved, which is conducive to the lightweight of the heat exchanger. In addition, the scheme for setting up the fins also includes a stacking process for the fins. This scheme only requires stacking the plates during assembly, which helps to simplify the assembly process of the heat exchanger 100 and reduce the manufacturing difficulty and cost of the heat exchanger 100; and the present application saves the assembly process for the fins, which can also improve the manufacturing efficiency of the heat exchanger 100 and save manufacturing time.

[0176] In other embodiments, the first plate 1 and the second plate 2 may be bonded. The first substrate 35 is a planar portion of the first plate 1, and the second substrate 36 is a planar portion of the second plate 2. In other embodiments, the recess 21 and the first high section 12 may be partially staggered, and the staggered setting means that the projections of the first high section 12 and the recess 21 on the plate surface of the first plate 1 overlap.

[0177] Combination Figure 48-Figure 58 The plate 5 includes a body 3 and a flange 4. The flange 4 is protruded relative to the body 3 and is arranged in the circumferential direction of the body 3. Along the length direction of the plate 5, the plate 5 includes a first end 51 and a second end 52.

[0178] The heat exchanger 100 includes a first channel 101, a second channel 102, a third channel 103, and a fourth channel 104. The first channel 101 and the third channel 103 are arranged near the first end 51, and the second channel 102 and the fourth channel 104 are arranged near the second end 52. In this embodiment, the plate 5 includes four corner holes 53, two of which are arranged near the first end 51, and the other two of which are arranged near the second end 52. The plates 5 are stacked, and the four corner holes of each plate are aligned along the stacking direction of the plates 5. The four corner holes are aligned along the stacking direction of the plates 5 to form four channels, namely the first channel 101, the second channel 102, the third channel 103, and the fourth channel 104.

[0179] In this embodiment, the first channel 101 is for the refrigerant to flow into the heat exchanger 100, and the second channel 102 is for the refrigerant to flow out of the heat exchanger 100. At the first channel 101 and the second channel 102, the first inter-plate channel S1 is open, and the first channel 101 and the second channel 102 are connected through the first inter-plate channel S1. At the first channel 101 and the second channel 102, the second inter-plate channel S2 is not open, and the first channel 101 and the second channel 102 are not connected to the second inter-plate channel S2. In this embodiment, the third hole 103 is for the coolant to flow into the heat exchanger 100, and the fourth hole 104 is for the coolant to flow out of the heat exchanger 100. At the third hole 103 and the fourth hole 104, the second inter-plate channel S2 is open, and the third hole 103 and the fourth hole 104 are connected through the second inter-plate channel S2. At the third hole 103 and the fourth hole 104, the first inter-plate channel S1 is not open, and the third hole 103 and the fourth hole 104 are not connected to the first inter-plate channel S1. The refrigerant flows in the first inter-plate channel S1, and the coolant flows in the second inter-plate channel S2, and the refrigerant and the coolant exchange heat. In other embodiments, the second hole 102 can also be used to supply the refrigerant to flow into the heat exchanger 100, and the first hole 101 can be used to supply the refrigerant to flow out of the heat exchanger 100. In other embodiments, the fourth hole 104 can also be used to supply the coolant to flow into the heat exchanger 100, and the third hole 103 can be used to supply the coolant to flow out of the heat exchanger 100.

[0180] The first substrate 35 includes a first plate surface 31 and a second plate surface 32, and the first plate surface 31 and the second plate surface 32 are arranged opposite to each other. The first plate 1 includes a plurality of first protrusions 11, and the first protrusions 11 protrude relative to the first plate surface 31 of the first plate 1 toward the second plate 2 on the adjacent side, and the first protrusions 11 protrude upward.

[0181] The plurality of first protrusions 11 are arranged in an array along a first direction E and a second direction F. The first direction E intersects with the second direction F. An angle α1 is formed between the first direction E and the second direction F. α1 is directed toward the length direction of the heat exchanger and is less than 90 degrees.

[0182] In this embodiment, there is a first low segment 13 between two adjacent first high segments 12. One end of the first low segment 13 is connected to the first high segment 12, and the other end of the first low segment 13 is connected to the first high segment 12. In this embodiment, along the F direction, two adjacent first convex portions 11 share one first high segment 12.

[0183] In this embodiment, the first high section 12 is located on the first plate surface 31 of the first plate 1, and the first high section 12 protrudes upward relative to the first plate surface 31 of the first plate 1. The first low section 13 is located on the first plate surface 31 of the first plate 1, and the first low section 13 protrudes upward relative to the first plate surface 31 of the first plate 1. In this embodiment, the minimum height of the first low section 13 from the first plate surface 31 of the first plate 1 is less than the maximum height of the first high section 12 from the first plate surface 31 of the first plate 1. Along the F direction, there is a second groove 122 between two adjacent first high sections 12. Along the E direction, there is a second groove 122 between two adjacent first high sections 12, and the second groove 122 is formed by the first low section 13. In this embodiment, along the F direction, the first high section 12 and the first low section 13 are alternately arranged, and the first high section 12 and the first low section 13 are connected together. The first high section 12 and the first low section 13 are both relatively raised structures. In this way, the raised structures are arranged more densely, which can increase the flow path of the refrigerant, increase the heat exchange area of ​​the refrigerant, and improve the heat exchange effect of the refrigerant and the coolant.

[0184] In other embodiments, one or more groups of two adjacent first high-level segments 12 may not have a first low-level segment 13 between them, and the two adjacent first high-level segments 12 in the group may be connected by a first plate surface 31 , and there may be a gap between the adjacent first high-level segments 12 in the group.

[0185] In other embodiments, along the F direction, there may be two or more first low segments 13 between two adjacent first high segments 12 , and along the E direction, there may be two or more first low segments 13 between two adjacent first high segments 12 .

[0186] In this embodiment, along the height direction of the heat exchanger 100, the minimum height of the first low section 13 from the first plate surface 31 of the first plate 1 is defined as H1, and the maximum height of the first high section 12 from the first plate surface 31 of the first plate 1 is defined as H2, and H1 is less than H2. In this embodiment, the first high section 12 includes a first top 121, and the distance between the first top 121 and the plate surface of the first plate 1 is H2. In this embodiment, the ratio of H1 to H2 is 0.25 to 0.75, and the height ratio of the first high section 12 and the first low section 13 is controlled. The top of the first high section 12 and the top of the recess 21 are welded, and the fluid can flow between the first low section 13 and the second substrate of the adjacent second plate 2, which is conducive to preventing the melting of the solder from blocking the space between the first low section 13 and the second substrate of the adjacent second plate 2.

[0187] Combination Figure 52-Figure 58, along the F direction and along the E direction, the first low-level segment 13 includes a trough 131, a first side wall 132 and a second side wall 133, one end of the first side wall 132 is connected to the first top 121 of the adjacent first high-level segment 12, the other end of the first side wall 132 is connected to the trough 131, one end of the second side wall 133 is connected to the trough 131, the other end of the second side wall 133 is connected to the first top 121 of the adjacent first high-level segment 12, and the trough 131 is located between the first side wall 132 and the second side wall 133. In this embodiment, the distance between the trough 131 and the first plate surface 31 of the first plate 1 is H1, and H1 is less than H2. When the first high-level segment 12 is provided on the first plate 1 and the first low-level segment 13 is not provided, when the first high-level segment 12 is provided relatively sparsely, the heat exchange effect between the refrigerant and the coolant is not good, and when the first high-level segment 12 is provided too densely, the first plate 1 is easy to be thinned, and the first plate 1 is difficult to form. In the present application, the first low-level segment 13 is connected to the adjacent first high-level segment 12. The first low-level segment 13 is arranged to be raised relative to the plate surface of the first plate 1. The plate 5 will not be too thin, and the plate 5 is easy to shape. The arrangement of the first low-level segment 13 can make the first high-level segment 12 arranged more densely, increase the flow path of the refrigerant, increase the heat exchange area between the refrigerant and the coolant, and improve the heat exchange effect of the heat exchanger; in addition, along the F direction, there is a second groove 122 between the two adjacent first high-level segments 12, and along the E direction, there is a second groove 122 between the two adjacent first high-level segments 12. The second groove 122 is located in the first low-level segment 13. The first high-level section 12 and the first low-level section 13 have a height difference. The setting of the first low-level section 13 increases the curved surface area of ​​the first plate 1, which can increase the heat exchange area between the refrigerant and the coolant, and improve the heat exchange effect of the heat exchanger 100.

[0188] In this embodiment, along the F direction, the first side wall 132 and the second side wall 133 are symmetrically arranged relative to the trough 131, along the E direction, the first side wall 132 and the second side wall 133 are symmetrically arranged relative to the trough 131, and the two adjacent first high-level sections 12 are symmetrically arranged relative to the trough 131, so that the structure of the first plate 1 is regular, which is convenient for controlling the flow direction of the refrigerant and also convenient for welding the first plate 1 and the second plate 2. In other embodiments, the first side wall 132 and the second side wall 133 can also be asymmetrically arranged relative to the trough 131, and the two adjacent first high-level sections 12 can also be asymmetrically arranged relative to the trough 131.

[0189] The second substrate 36 includes a third plate surface 33 and a fourth plate surface 34, and the third plate surface 33 and the fourth plate surface 34 are arranged opposite to each other, and the third plate surface 33 is closer to the second plate surface 32 of the second plate piece 2 on the adjacent side relative to the fourth plate surface 34. In this embodiment, the recess 21 of the second plate piece 2 is located on the third plate surface 33, and the recess 21 protrudes toward the first plate piece 1 on the adjacent side relative to the third plate surface 33 of the second plate piece 2, and the protruding direction of the recess 21 is consistent with the protruding direction of the first high-level section 12. There is a first groove 212 between adjacent recesses 21, and the recess 21 has a groove 211 facing the first plate piece 1 on the other adjacent side.

[0190] In this embodiment, a plurality of recesses 21 are arranged along the F direction, and the recesses 21 are arranged in a plurality of lines along the F direction. Along the F direction, the recesses 21 are arranged in parallel with the first convex portion 11. A plurality of recesses 21 are also arranged along the E direction, and the recesses 21 are arranged in a plurality of lines along the E direction, and the recesses 21 are arranged in parallel with the first convex portion 11 along the E direction. The recesses 21 are arranged in parallel with the first high-level section 12, which facilitates the welding of the first plate 1 and the second plate 2. The height of the recess 21 from the third plate surface of the second plate 2 is equal to the height of the first high-level section 12 from the first plate surface 31 of the first plate 1. In other embodiments, the height of the recess 21 from the third plate surface of the second plate 2 may also be greater than or less than the height of the first high-level section 12 from the first plate surface 31 of the first plate 1.

[0191] In this embodiment, two adjacent plates 5 are welded and fixed, and the first top 121 of the concave portion 21 and the third plate surface 33 of the second plate 2 are welded and fixed. In this embodiment, the concave portion 21 and the first convex portion 11 are arranged in parallel and staggered along the F direction, and the concave portion 21 and the first convex portion 11 are arranged in parallel and staggered along the E direction. Parallel arrangement and staggered arrangement means that along the F direction, the projections of the first high section 12 and the concave portion 21 on the first plate surface 31 do not overlap and are parallel, and along the E direction, the projections of the first high section 12 and the concave portion 21 on the first plate surface 31 do not overlap and are parallel. Along the height direction of the heat exchanger, the concave portion 21 and the first base plate 35 are arranged relative to each other, and the presence of the groove 211 of the concave portion 21 is conducive to strengthening the boiling heat transfer of the refrigerant and improving the heat exchange effect of the refrigerant and the coolant. In this embodiment, the top of the first high section 12 is a plane structure, which is conducive to increasing the welding surface with the second plate 2 on the adjacent side and enhancing the welding strength of the heat exchanger. In other embodiments, the first top 121 can also be an arc structure. In other embodiments, the concave portion 21 and the first convex portion 11 may also be arranged in parallel and partially staggered, and the parallel arrangement and partially staggered arrangement means that along the F direction, the projections of the first high section 12 and the concave portion 21 on the first plate surface 31 overlap and are parallel. In this way, the heat exchanger can also have a better heat exchange effect.

[0192] In other embodiments, part of the recess 21 may be arranged along the F direction. In other embodiments, the recess 21 may not be arranged along the F direction, the recess 21 and the first convex portion 11 are not arranged in parallel, and the recess 21 and the first substrate 35 are partially aligned along the height direction of the heat exchanger. In other embodiments, part of the recess 21 may be arranged along the E direction. In other embodiments, the recess 21 may not be arranged along the E direction, the recess 21 and the first convex portion 11 are not arranged in parallel, and part of the recess 21 and the first substrate 35 are partially aligned along the height direction of the heat exchanger.

[0193] The recess 21 has a groove 211 on the second plate 2 facing the other adjacent side. The groove 211 is a part of the refrigerant flow channel. The refrigerant exchanges heat with the coolant. The existence of the groove 211 is beneficial to strengthen the boiling heat transfer of the refrigerant and improve the heat exchange effect of the heat exchanger 100. In addition, when the first plate 1 is only provided with the first high section 121 and the first plate 1 does not have the first low section 13, the first plate 1 and the second plate 2 have similar structures, and the convex structure on the first plate 1 is relatively sparse. In the present application, the first high section 12 and the first low section 13 form a dense convex structure, and the recess and the dense convex structure match, which can better improve the heat exchange effect of the refrigerant and the coolant.

[0194] In this embodiment, along the F direction, adjacent first high-level sections 121 have a second groove 122, and along the E direction, two adjacent first high-level sections 121 have a second groove 122. Along the height direction of the heat exchanger, the groove 211 and the first substrate 35 are aligned to form a first space S11 (not shown in the figure) between the wall of the groove 211 and the first substrate 35, which is part of the first inter-plate channel S1. Along the E direction and the F direction, there is a second groove 122 between two adjacent first high sections 12, and the second groove 122 is formed by the first low section 13. The height of the recess 21 from the third plate surface 33 is equal to the height of the first high section 12 from the first plate surface 31, and the height of the first low section 13 from the first plate surface 31 is less than the height of the first high section 12 from the first plate surface 31. The height of the first low section 13 is less than the height of the recess 21. A second space S12 (not shown in the figure) is formed between the first low section 13 and the second substrate 36. The width of the second space S12 is less than the width of the first space S11. The refrigerant flows from the second space S12 to the first space S11, and then to the second space S12. The width of the refrigerant flow channel changes from narrow to wide and then from wide to narrow, which can further assist the transport of bubbles after the refrigerant "nucleates" and promote boiling enhanced heat exchange. In addition, the setting of the first high-position section 12 increases the area of ​​the first plate 1, and the setting of the recess 21 increases the area of ​​the second plate 2. The first plate 1 and the second plate 2 are used for heat transfer between the refrigerant and the coolant, which increases the heat transfer area of ​​the refrigerant and the coolant, and can further improve the heat exchange of the refrigerant and the coolant.

[0195] In addition, there is a first low section 13 between adjacent first high sections 12, and the first low section 13 protrudes relative to the first plate 1 toward the second plate 2 on the adjacent side, so that the distance between the first low section 13 and the second plate 2 on the adjacent side is small, so that the structure of the heat exchanger 100 is relatively compact; when the first plate 1 does not have the first low section 13, along the F direction, the depth of the second groove 122 between the two adjacent first high sections 12 is the height H2 of the first top 121 of the first high section 12 from the first plate surface 31, and when the first plate 1 has the first low section 13, the depth of the second groove 122 between the two adjacent first high sections 12 is the height H1 of the trough 131 of the first low section 13 from the first plate surface 31, H1 is smaller than H2, and the setting of the first low section 13 makes the flow space width of the refrigerant formed by the alignment of the second groove 122 and the second base plate 36 smaller, so that the refrigerant can have a higher pressure drop, the flow rate of the refrigerant is fast, and it is beneficial to enhance the heat exchange of the refrigerant. The first high-level section 12 and the recess 21 have different structures. The first high-level section 12 of the first plate 1 and the recess 21 of the second plate 2 on the adjacent side have a high degree of asymmetry, which is beneficial to increase the turbulence degree and boiling nucleation state of the refrigerant, thereby achieving high heat exchange performance of the heat exchanger 100.

[0196] In addition, in order to improve the heat exchange effect of the heat exchanger, fins are usually arranged between the plates 5. The flow channels formed by the fins are difficult to clean. In the present application, the first plate 1 and the second plate 2 are stamped structures, and the heat exchanger 100 is easy to clean.

[0197] Combination Figure 51-Figure 53 In this embodiment, the first plate 1 further includes a third protrusion 37 , which protrudes away from the second plate 2 relative to the first plate surface 31 and the first substrate 35 , and includes a second high section 17 and a second low section 18 .

[0198] The second low section 18 is recessed toward the first plate 1 relative to the second substrate 36 . Along the vertical direction with the second substrate 36 , the second high section 17 is closer to the second plate 2 than the first low section 13 . The second high section 17 includes a second top 171 , and the second top 171 is flush with the second plate surface 32 .

[0199] In this embodiment, the second high segment 17 and the second low segment 18 are arranged along the F direction, and the second high segment 17 and the second low segment 18 are arranged along the E direction. In this embodiment, along the F direction, there is a second low segment 18 between two adjacent second low segments 18, one end of the second low segment 18 is connected to an adjacent second high segment 17, and the other end of the second low segment 18 is connected to another adjacent second high segment 17. In this embodiment, along the E direction, there is a second low segment 18 between two adjacent second low segments 18, one end of the second low segment 18 is connected to an adjacent second high segment 17, and the other end of the second low segment 18 is connected to another adjacent second high segment 17, and there is a second groove 122 between adjacent second high segments 17, and the second groove 122 is located in the second low segment 18. In this embodiment, the structure of the second high segment 17 is substantially the same as that of the first high segment 12, and the structure of the second low segment 18 is substantially the same as that of the first low segment 13. Substantially the same includes identical and similar, and substantially the same refers to substantially identical size and shape. In other embodiments, the structure of the second high segment 17 may be different from that of the first high segment 12. In other embodiments, part of the second high segment 17 and the second low segment 18 may be arranged along the F direction, and part of the second high segment 17 and the second low segment 18 may be arranged along the E direction.

[0200] The first plate 1 and the second plate 2 are fixedly connected, and a second inter-plate channel s2 is provided between the first plate 1 and the second plate 2 on the other adjacent side. In this embodiment, the second high-level section 17 of the first plate 1 and the recess 21 of the second plate 2 on the other adjacent side are welded and fixed. In this embodiment, the second high-level section 17 includes a second top 171, and the recess 21 includes a third top 213, and the second top 171 and the third top 213 are in contact and welded. In this embodiment, the third top 213 is a planar structure, and the second top 171 is also a planar structure, which is conducive to increasing the welding surface of the third top 213 and the second top 171, and enhancing the welding strength of the heat exchanger. In other embodiments, the third top 213 can also be an arc-shaped structure, and the second top 171 can also be an arc-shaped structure, etc.

[0201] There is a first groove 212 between adjacent recesses 21, and there is a third groove 172 between adjacent second high-level sections 17. The third groove 172 is located in the second low-level section 18. Along the height direction of the heat exchanger, part of the first groove 212 and the first substrate 35 are arranged opposite to each other, forming a part of the second inter-plate channel s2 between the wall of the first groove 212 and the first substrate 35. Part of the first groove 212 and the third groove 172 are arranged in alignment, and part of the first groove 212 and the third groove 172 are aligned to form a part of the second inter-plate channel s2. The depth of the first groove 212 is consistent with the height of the recess 21. The space formed by the first groove 212 and the third groove 172 is relatively large, which provides a larger flow space for the flow of the coolant, so that the coolant has a lower pressure drop and a lower flow rate of the coolant, which can improve the heat exchange effect of the coolant and the refrigerant. The second high-level section 17 and the second low-level section 18 form a dense convex structure, which increases the heat exchange area of ​​the coolant and can further improve the heat exchange effect of the coolant and the refrigerant. In other embodiments, the second high section 17 and the recessed portion 21 may also be fixed by bonding.

[0202] Combination Figure 7-Figure 10 , α1 is the first distribution angle of the first high segment 12, α1 is also the first distribution angle of the first low segment 13, and α1 can be 15°~75°. In this embodiment, α1 is 20°~35°, including 20°~35. When α1 is other values, 20°~35, the first high segment 12 can be set relatively densely, which is beneficial to improve the heat exchange efficiency of the refrigerant and the coolant. In this embodiment, the first distribution angle of the second high segment 17 is consistent with the first distribution angle of the first high segment 12, and the distribution angle of the second low segment 18 is also consistent with the first distribution angle of the first low segment 13, which is beneficial to improve the density of the protruding structure, increase the heat exchange area of ​​the coolant, increase the heat exchange area of ​​the coolant and the refrigerant, and improve the heat exchange effect of the heat exchanger 100. In other embodiments, the first distribution angle of the second high segment 17 and the first distribution angle of the first high segment 12 may also be inconsistent, and the first distribution angle of the second low segment 18 and the first distribution angle of the first low segment 13 may also be inconsistent.

[0203] α1 is the second distribution angle of the first high-level segment 12, and α1 is also the second distribution angle of the first low-level segment 13, so that the protrusion structure can be arranged relatively densely, which is beneficial to improving the heat exchange efficiency of the refrigerant and the coolant. In this embodiment, the second distribution angle of the second high-level segment 17 is consistent with the second distribution angle of the first high-level segment 12, and the distribution angle of the second low-level segment 18 is also consistent with the second distribution angle of the first low-level segment 13, which is beneficial to improve the density of the protrusion structure, increase the heat exchange area of ​​the coolant, increase the heat exchange area of ​​the coolant and the refrigerant, and improve the heat exchange effect of the heat exchanger 100.

[0204] The recesses 21 are arranged in a line along the F direction, and the first distribution angle of the recesses 21 is also α1, and α1 is 20° to 35°, including 20° to 35. The recesses 21 can be arranged relatively densely, which is beneficial to increase the density of the recesses 21, increase the boiling heat transfer effect of the refrigerant, improve the heat exchange efficiency of the refrigerant and the coolant, and improve the heat exchange effect of the heat exchanger 100.

[0205] The first plate 1 includes a first substrate 35 and a plurality of first high sections 12. The first high sections 12 are protruded relative to the first substrate 35. Along the width direction of the heat exchanger 100, the distance between the center points of two adjacent first high sections 12 is d1. The ratio of d1 to the height H2 of the top of the first high section 12 from the plate surface of the first substrate 35 is 1.5 to 6.

[0206] Combination Figure 58-Figure 73 In this embodiment, along the width direction of the plate 5, the distance between two adjacent first high sections 12 is d1, d1 is the distance between the center points of the two adjacent first high sections 12, and d1 is the distance between the two adjacent first high sections 12 in the width direction. The ratio of the distance in the width direction between adjacent first high sections 12 and the maximum height of the first high section 12 from the plate surface of the first plate 1 can be 1.5-6, that is, the ratio between d1 and H2 is 1.5-6. In this embodiment, the ratio of the distance in the width direction between adjacent first high sections 12 and the maximum height of the first high section 12 from the plate surface of the first plate 1 is 2.3-5.5, that is, the ratio between d1 and H2 is 2.3-5.5. The higher the height of the first high section 12, the sparser the first high section 12 should be, otherwise the high and dense first high section 12 will cause a large thinning rate at the top of the first high section 12, so that the plate 5 is not easy to form, and the first high section 12 is too sparse to increase the turbulence of the refrigerant and enhance the heat exchange. When the ratio between d1 and H2 is 2.3 to 5.5, the first high-level segment 12 can be arranged relatively densely, which is beneficial to increasing the turbulence effect of the first high-level segment 12 on the refrigerant, and the thinning rate of the first plate 1 will not be too low, so that the second plate 2 is easy to form. The ratio between d1 and H2 is applicable to point waves and herringbone waves.

[0207] In this embodiment, along the width direction of the plate 5, the ratio of the width direction distance between adjacent second high sections 17 to the height of the second high section 17 is also 2.3 to 5.5, so that the second high section 17 can be arranged relatively densely, which is conducive to increasing the turbulent effect of the second high section 17 on the coolant, and the second plate 2 is also easy to form. In this embodiment, the ratio of the width direction distance between adjacent second high sections 17 to the height of the second high section 17 is the same as the ratio between d1 and H2, so that the first plate 1 and the second plate 2 are easy to form, and the flow rates of the refrigerant and the coolant are adapted, which is conducive to improving the heat exchange efficiency of the coolant and the refrigerant. In other embodiments, the ratio of the width direction distance between adjacent second high sections 17 to the maximum height of the second high section 17 can also be 1.5 to 2.3 or 5.5 to 6.

[0208] In this embodiment, along the width direction of the plate 5, the distance between adjacent recesses 21 is d2, and d2 is the distance between the center points of adjacent recesses 21. In this embodiment, d2 is the distance between the third tops 213 of adjacent recesses 21, d2 is the distance between adjacent recesses 21 in the width direction, and the distance between the third top 213 of the recess 21 and the plate surface of the second plate 2 is H3. In this embodiment, the ratio of d2 to H3 is also 2.3 to 5.5, so that the recesses 21 can be arranged more densely, and the second plate 2 is also easy to shape; in addition, the recesses 21 can be arranged more densely, which is conducive to improving the boiling heat transfer on the refrigerant side, and is also conducive to increasing the flow path of the coolant, and improving the heat exchange effect of the heat exchanger 100. In this embodiment, the ratio of d2 and H3 is the same as the ratio of d1 and H2, so that the structures of the first plate 1 and the second plate 2 can be more coordinated, and the refrigerant side can have a suitable flow space, the refrigerant has a suitable pressure drop, and the refrigerant has a higher flow rate; this can also allow the coolant to have a suitable flow space and pressure drop, the coolant has a lower flow rate, and the pressure drops on the coolant side and the refrigerant side are relatively suitable, which is beneficial to improving the heat exchange efficiency of the coolant and the refrigerant.

[0209] In another embodiment, along the F direction, there is no second low section 18 between the second high sections 17, the second high sections 17 are convexly arranged downward relative to the second base plate 36 of the second plate 2, and a third groove 172 is provided between two adjacent second high sections 17. The second top 171 of the second high section 17 and the third top 213 of the concave portion 21 are in contact and fixed by welding, so that the boiling heat transfer of the refrigerant can be enhanced and better heat exchange between the refrigerant and the coolant can be achieved.

[0210] In this embodiment, the first plate 1 includes a first rib 14, which extends in a curved shape along the length direction of the first plate 1, and the first rib 14 is welded and fixed to the plate surface of the second plate 2. The arrangement of the first rib 14 can make the refrigerant flow in a U-shaped loop, thereby increasing the heat exchange effect between the refrigerant and the coolant. The arrangement of the first rib 14 is curved, which increases the flow resistance of the flow path close to both sides of the first rib 14, reduces the distribution of the refrigerant on both sides of the first rib 14, and makes the distribution of the refrigerant in the first inter-plate channel S1 more uniform, which is beneficial to improving the heat exchange performance of the heat exchanger.

[0211] In this embodiment, the first plate 1 and the second plate 2 are both provided with ribs to increase the flow path of the refrigerant and the coolant and improve the heat exchange. The second plate 2 includes a second rib 22, and the second rib 22 is arranged so that the coolant flows in a U-shaped loop. The second rib 22 extends in a curved shape along the length direction of the first plate 2, and the second rib 22 and the first rib are arranged roughly parallel, and roughly parallel includes parallel and approximately parallel. Along the height direction of the heat exchanger 100, the first rib 14 and the second rib 22 are arranged in a staggered manner, and the staggered arrangement means that the projections of the first rib 14 and the second rib 22 on the first plate surface do not overlap, so that it is convenient to weld and fix the first rib 14 and the second plate 2, and to weld and fix the second rib 22 and the first plate 1. The top of the first rib 14 and the fourth plate surface 34 of the second plate 2 on the adjacent side are welded and fixed, and the top of the second rib 22 and the second plate surface 32 of the first plate 1 on the adjacent side are welded and fixed.

[0212] In this embodiment, the first rib 14 is located in the body 3, the first rib 14 is located in the first plate surface 31 of the first plate 1, the first rib 14 protrudes toward the second plate 2 on the adjacent side relative to the first plate surface 31 of the first plate 1, and the first rib 14 has a first groove 141 toward the third plate surface 33 of the second plate 2 on the other side. Along the width direction of the first plate 1, on the side of the first plate surface 31 of the first plate 1, there is a gap between the two sides of the first rib 14 and the first protrusion 11, and the gap can allow the refrigerant to flow. In this embodiment, the second rib 22 is located in the body 3, the second rib 22 is located in the third plate surface 33 of the second plate 2, the second rib 22 protrudes toward the first plate 1 on the adjacent side relative to the plate surface of the second plate 2, and the second rib 22 has a second groove 221 toward the first plate surface 31 of the first plate 1 on the other side. Along the width direction of the second plate 2, on the third plate surface 33 side of the second plate 2, there is a gap between the two sides of the second rib 22 and the recess 21, and the gap can allow the coolant to flow.

[0213] In this embodiment, the first channel 101 is the inflow channel of the refrigerant, and the second channel 102 is the outflow channel of the refrigerant. The refrigerant flows into the heat exchanger 100 from the first channel 101, first flows on the first side 15 of the plate 5, then flows around the first rib 14 to the second side 16 of the plate 5, and flows out of the heat exchanger 100 from the second channel 102. The refrigerant flows around the first rib 14 in a U-shaped line. The first rib 14 is provided so that the refrigerant flows around the first rib 14 in a U-shaped loop, so that the refrigerant has two flow sections, which can increase the flow path of the refrigerant, increase the heat exchange area between the refrigerant and the coolant, and improve the effect of the heat exchanger 100. In addition, the first rib 14 is provided so that the first channel 101 and the second channel 102 are located on the same side of the width of the heat exchanger 100, which is convenient for the heat exchanger 100 to cooperate with other components, such as the expansion valve.

[0214] Combination Figure 1 , Figure 58-Figure 73 In this embodiment, the third channel 103 is the inflow channel of the coolant, and the fourth channel 104 is the outflow channel of the coolant. The coolant flows into the heat exchanger 100 from the third channel 103, first flows on the first side 15 of the second plate 2, then flows around the second rib 22 to the second side 16 of the second plate 2, and flows out of the heat exchanger 100 from the fourth channel 104. The coolant flows around the second rib 22 in a U-shaped line. The setting of the second rib 22 can make the coolant have two flow sections, which can increase the flow path of the coolant and improve the heat exchange effect of the coolant and the refrigerant. In addition, the setting of the second rib 22 makes the third channel 103 and the fourth channel 104 located on the same side of the width of the heat exchanger 100, which is convenient for the heat exchanger 100 to cooperate with other components.

[0215] In this embodiment, the first rib 14 is arranged along the length direction of the first plate 1, one end of the first rib 14 is connected to the flange 4 near the first end 51, the other end of the first rib 14 is not connected to the flange 4 near the second end 52, and there is a gap between the other end of the first rib 14 and the flange 4 near the second end 52 for the flow of refrigerant. In this embodiment, along the width direction of the plate 5, the first plate 1 includes a first side 15 and a second side 16, the first rib 14 is located between the first side 15 and the second side 16, and the first side 15 and the second side 16 are located on the first plate surface 31. The second rib 22 is arranged along the length direction of the plate 5, one end of the second rib 22 is connected to the flange 4 near the second end 52, the other end of the second rib 22 is not connected to the flange 4 near the first end 51, and there is a gap between the other end of the second rib 22 and the flange 4 near the first end 51 for the flow of coolant. The second plate 2 includes a third side 23 and a fourth side 24 . The third side 23 and the fourth side 24 are located on the third plate surface 33 . The second rib 22 is located between the third side 23 and the fourth side 24 .

[0216] Combination Figure 52-Figure 61In this embodiment, the first rib 14 is serrated. The first rib 14 includes a first portion 142 and a second portion 143, which are alternately arranged along the length direction of the first rib 14, and adjacent first portions 142 and second portions 143 are connected. The first portion 142 and the second portion 143 are arranged at an angle, and the first portion 142 and an adjacent second portion 143 form a first recess (not shown in the figure), the first recess protrudes toward the first side 15 of the first plate 1, and the first recess protrudes toward the second side 16 of the first plate 1. When the refrigerant flows into the first channel 101 and flows around the first rib 14 to the second channel, the refrigerant near both sides of the first rib 14 flows along the first recess, which increases the flow resistance of the flow path near both sides of the first rib 14, reduces the distribution of the refrigerant on both sides of the first rib 14, and makes the distribution of the refrigerant in the first inter-plate channel S1 more uniform, which is beneficial to improving the heat exchange performance of the heat exchanger.

[0217] In this embodiment, the second rib 22 is also serrated, and the second rib 22 and the first rib 14 are arranged roughly in parallel. The second rib 22 includes a third portion 222 and a fourth portion 223, and the third portion 222 and the fourth portion 223 are alternately arranged along the length direction of the second rib 22, and the adjacent third portions 222 and fourth portions 223 are connected. The third portion 222 and the fourth portion 223 are arranged at an angle, and the third portion 222 and an adjacent fourth portion 223 form a second recess (not shown in the figure), the second recess protrudes toward the fourth side of the second plate, and the second recess is recessed toward the third side of the second plate. The first portion 142 and the third portion 222 are arranged roughly in parallel, and the second portion 143 and the fourth portion 223 are arranged roughly in parallel. When the coolant flows in from the third channel 103 and flows around the second rib 22 to the fourth channel, the coolant near the two sides of the second rib 22 flows along the second recess, which increases the flow resistance of the flow path near the two sides of the second rib 22, reduces the distribution of the coolant on both sides of the second rib 22, and makes the distribution of the coolant in the second inter-plate channel S2 more uniform, which is beneficial to improving the heat exchange performance of the heat exchanger.

[0218] In this embodiment, the first part 142, the second part 143, the third part 222 and the fourth part 223 are all straight structures, and the first concave part and the second concave part are also straight. In this embodiment, the first part 142 and the second part 143 form an angle greater than or equal to 90°, and the third part 222 and the fourth part 223 form an angle greater than or equal to 90°. The first part 142 and the second part 143 are connected, and the first rib 14 forms a zigzag shape, which increases the flow resistance of the refrigerant near the first rib 14, avoids too much refrigerant flowing through here, thereby extending the flow path of the refrigerant and improving the heat exchange effect. The third part 222 and the fourth part 223 are connected, and the second rib 22 forms a zigzag shape, which increases the flow resistance of the coolant near the second rib 22, avoids too much coolant flowing through here, thereby extending the flow path of the coolant and improving the heat exchange effect. In other embodiments, the connection between the first portion 142 and the second portion 143 may be arc-shaped, and the connection between the third portion 222 and the fourth portion 223 may be arc-shaped, wherein the arc may be a circular arc or other arc shapes.

[0219] In other embodiments, the included angle between the first portion 142 and the second portion 143 may also be an acute angle less than 90 degrees, and the included angle between the third portion 222 and the fourth portion 223 may also be an acute angle less than 90 degrees.

[0220] In another embodiment, the first portion 142, the second portion 143, the third portion 222 and the fourth portion 223 are all arc-shaped structures, the first recessed portion and the second recessed portion are also arc-shaped, the first portion 142 and the third portion 222 are arranged roughly in parallel, and the second portion 143 and the fourth portion 223 are arranged roughly in parallel, so that the distribution of the refrigerant and the coolant can be more uniform, and the heat exchange performance of the heat exchanger can be improved. Among them, the arc-shaped structure can be a circular arc or other arcs, so that the first rib portion 14 and the second rib portion 22 form a winding shape.

[0221] In another embodiment, the first part 142 is an arc-shaped structure, the second part 143 is a straight structure, the third part 222 is an arc-shaped structure, and the fourth part 223 is a straight structure. The first part 142 and the third part 222 are arranged roughly in parallel, and the second part 143 and the fourth part 223 are arranged roughly in parallel. This can also make the distribution of the refrigerant and the coolant more uniform, thereby improving the heat exchange performance of the heat exchanger.

[0222] In other embodiments, the first rib 14 may also be in a curved wave shape, and the second rib 22 may also be in a curved wave shape.

[0223] In this embodiment, along the width direction of the plate 5, the first rib 14 is offset and the second rib 22 is centered. The first plate 1 and the second plate 2 are welded and fixed. The top of the first rib 14 and the fourth plate surface 34 of the second plate 2 on the adjacent side are welded and fixed. The top of the second rib 22 and the second plate surface 32 of the first plate 1 on the adjacent side are welded and fixed.

[0224] In this embodiment, along the width direction of the plate 5, the width of the third side 23 is equal to the width of the fourth side 24, so that the coolant can have a suitable pressure drop and a suitable flow rate, and the coolant can effectively exchange heat with the refrigerant.

[0225] In this embodiment, along the width direction of the plate 5, the width of the first side 15 is smaller than the width of the second side 16. In this embodiment, the first side 15 is close to the inlet channel of the refrigerant, and the first side 15 is the first process section of the refrigerant. The second side 16 is close to the outlet channel of the refrigerant, and the second side 16 is the second process section of the refrigerant. When the refrigerant enters the heat exchanger 100, the dryness is low, and the heat exchange effect between the refrigerant and the coolant is good. After the refrigerant works for a period of time, the temperature of the refrigerant increases, and the dryness of the refrigerant becomes higher. The wider flow channel of the second side 16 is conducive to the flow of the refrigerant, controls the refrigerant to have a higher pressure drop, and reduces the heat exchange performance degradation caused by the enthalpy loss of the refrigerant. In other embodiments, the width of the first side 15 can also be equal to or greater than the width of the second side 16.

[0226] In this embodiment, along the width direction of the plate 5, the width of the third side 23 is equal to the width of the fourth side 24, so that the coolant can have a suitable pressure drop and a suitable flow rate, and the coolant can effectively exchange heat with the refrigerant.

[0227] Along the width direction of the plate 5, the first rib 14 is offset, the second rib 22 is centered, the first plate 1 and the second plate 2 are welded and fixed, the top of the first rib 14 and the fourth plate surface 34 of the second plate 2 on the adjacent side are welded and fixed, and the top of the second rib 22 and the second plate surface 32 of the first plate 1 on the adjacent side are welded and fixed. Along the width direction of the heat exchanger, the first rib 14 is close to the third side 23 of the second plate 2, the second rib 22 is close to the second side 16 of the first plate 1, and the second groove 221 is close to the second flow section of the refrigerant. The dryness of the refrigerant in the second flow section is high, and the heat exchange effect of the refrigerant is poor. The second groove 221 is part of the refrigerant flow channel, and the flow of the refrigerant in the second groove 221 is blocked. Placing the second groove 221 close to the second flow section of the refrigerant is conducive to reducing the influence of the second groove 221 on the heat exchange effect of the refrigerant. In this embodiment, the first rib 14 and the second rib 22 have the same height. Along the height direction of the heat exchanger, the first side wall 144 of the first rib 14 and the second side wall 224 of the second rib 22 are aligned, which is conducive to reducing the gap between the first rib 14 and the second rib 22, reducing the refrigerant flowing into the gap between the first rib 14 and the second rib 22, and improving the heat exchange effect of the heat exchanger 100. In addition, the gap between the first rib 14 and the second rib 22 is located in the second flow section of the refrigerant, which is conducive to preventing the pressure drop of the refrigerant from being low. In other embodiments, the width of the third side 23 and the width of the fourth side 24 may also be different.

[0228] In other embodiments, the first plate 1 may be provided with the first rib 14, and the second plate 2 may not be provided with the second rib 22; or, the first plate 1 may not be provided with the first rib 14, and the second plate 2 may be provided with the second rib 22, which may also improve the heat exchange effect between the refrigerant and the coolant.

[0229] In this embodiment, along the length direction of the heat exchanger 100, the first channel 101 and the third channel 103 are located on the same side of the heat exchanger 100, and the second channel 102 and the fourth channel 104 are located on the same side of the heat exchanger 100, so that the flow directions of the refrigerant and the coolant are opposite, and the refrigerant and the coolant are countercurrent, which is conducive to improving the heat exchange effect of the two. In other embodiments, along the length direction of the heat exchanger 100, the first channel 101 and the fourth channel 104 can also be located on the same side of the heat exchanger 100, and the second channel 102 and the third channel 103 can be located on the same side of the heat exchanger 100, so that the heat exchange of the refrigerant and the coolant can also be achieved.

[0230] The first plate 1 includes a first protrusion 11, which protrudes toward the second plate 2, and the first protrusion 11 is arranged along the F direction. Part of the first rib 14 extends parallel to the F direction, that is, the extension direction of part of the first rib 14 is consistent with the arrangement direction of the first protrusion 11, so that the flow path of the refrigerant near both sides of the first rib 14 can be consistent with the flow path between the first protrusions 11, which is beneficial to reducing the resistance of the refrigerant flow, making the refrigerant flow smoother, and making the refrigerant and the coolant have a higher heat exchange effect.

[0231] In this embodiment, the first portion 142 extends in a direction parallel to the F direction, that is, the extension direction of the first portion 142 is parallel to the arrangement direction of the first convex portion 11, and the second portion 143 extends in a direction parallel to the E direction, that is, the extension direction of the first portion 142 is also parallel to the arrangement direction of the first convex portion 11. This arrangement can make the shape of the first rib 14 consistent with the flow direction of the refrigerant, avoid the first rib 14 blocking the flow of the refrigerant, reduce the flow resistance of the refrigerant flow, make the refrigerant flow more smoothly, and make the refrigerant and the coolant have a higher heat exchange effect. In this embodiment, the second rib 22 is also Z-shaped and wavy. The second rib 22 includes a third portion 222 and a fourth portion 223. The third portion 222 extends in a direction parallel to the F direction, and the fourth portion 223 extends in a direction parallel to the E direction. This arrangement can make the shape of the second rib 22 consistent with the flow direction of the coolant, avoid the second rib 22 blocking the flow of the coolant, reduce the flow resistance of the coolant flow, make the coolant flow more smoothly, and improve the heat exchange effect of the coolant and the coolant.

[0232] The angle between the F direction and the E direction is α1, and α1 is 15° to 75°, so that the first protrusion 11 and the recess 21 can be arranged more densely, which is conducive to increasing the heat exchange area between the refrigerant and the coolant and improving the heat exchange effect. In this embodiment, α1 is 20° to 35°, so that the first protrusion 11 and the recess 21 can be arranged more densely, and the heat exchange effect of the heat exchanger 100 is better; in addition, the first part 142 and the third part 222 extend along the E direction, and the second part 143 and the fourth part 223 extend along the F direction. Such an angle setting is conducive to making the first rib 14 and the second rib 22 form a more winding shape, increasing the flow resistance of the refrigerant near the first rib 14, avoiding excessive refrigerant from flowing there, thereby extending the flow path of the refrigerant, improving the heat exchange effect, and increasing the flow resistance of the coolant near the second rib 22, extending the flow path of the coolant, and improving the heat exchange effect.

[0233] In other embodiments, the first portion 142 may extend in a direction parallel to the F direction, the second portion 143 may not extend in a direction parallel to the E direction, the third portion 222 may be arranged in conjunction with the first portion 142 , and the fourth portion 223 may be arranged in conjunction with the second portion 143 . For example, the first portion 142, the second portion 143, the third portion 222 and the fourth portion 223 are all straight structures, and the first portion 142 and the third portion 222 extend in a direction parallel to the F direction, that is, the arrangement directions of the first portion 142, the third portion 222 and the first convex portion 11 are consistent, and the second portion 143 and the fourth portion 223 do not extend in a direction parallel to the E direction, that is, the arrangement directions of the second portion 143 and the first convex portion 11 are inconsistent, and the arrangement directions of the fourth portion 223 and the first convex portion 11 are inconsistent; or, the second portion 143 is an arc-shaped structure, the first portion 142 is a straight structure, the fourth portion 223 is an arc-shaped structure, and the third portion 222 is a straight structure. The first portion 142 and the third portion 222 extend in a direction parallel to the F direction, and the second portion 143 and the fourth portion 223 do not extend in a direction parallel to the E direction.

[0234] When the height of the first high-position section 12 is different from the height of the recess 21, the height H2 of the first top 121 from the plate surface of the plate 5 is less than the height H3 of the third top 213 from the plate surface of the plate 5, the height of the second rib 22 is less than the height of the first rib 14, the depth of the first groove 141 of the second rib 22 toward the adjacent first plate 1 on the other side is less than the depth of the second groove 221 of the second rib 22 toward the adjacent second plate 2 on the other side, and the depth of the first groove 141 corresponding to the refrigerant side is less than the depth of the second groove 221 corresponding to the coolant side, which is conducive to reducing the flow space on the refrigerant side, increasing the flow space on the coolant side, making the refrigerant have a higher pressure drop, reducing the pressure drop of the coolant, and making the heat exchange efficiency between the coolant and the refrigerant better. In other embodiments, the height of the second rib 22 may also be greater than the height of the first rib 14, and the depth of the first groove 141 corresponding to the refrigerant side is greater than the depth of the second groove 221 corresponding to the coolant side. In other embodiments, H2 may also be greater than H3.

[0235] Combination Figure 53-Figure 62, the first high section 12 is arranged close to the first rib 14, and the outer diameter of the first high section 12 close to the first rib 14 is greater than the outer diameter of the first high section 12 away from the first rib 14. In this embodiment, the second plate 2 includes an A zone (not shown in the figure) and a B zone (not shown in the figure), the B zone has two, the A zone is located between the two B zones, the first rib 14 is located in the A zone, and the B zone is far away from the first rib 14 relative to the A zone. In this embodiment, the first high section 12 in the A zone is arranged close to the first rib 14, which can reduce the gap between the first high section 12 and the first rib 14, reduce the amount of refrigerant flowing into the gap, thereby reducing the bypass of the refrigerant and improving the heat exchange effect of the heat exchanger 100. In this embodiment, the outer diameter of the first high section 12 in the A zone is greater than the outer diameter of the first high section 12 in the B zone, which can also reduce the gap between the first high section 12 and the first rib 14, reduce the bypass of the refrigerant, and improve the heat exchange effect of the heat exchanger 100. In other embodiments, the outer diameter of the first high section 12 in the A zone may also be equal to or smaller than the outer diameter of the first high section 12 in the B zone.

[0236] In this embodiment, the second high section 17 of the A zone is arranged close to the first rib 14, so that the gap between the second high section 17 and the first rib 14 can be reduced, the bypass of the coolant can be reduced, and the heat exchange effect of the heat exchanger 100 can be improved. Along the length direction of the plate 5, the outer diameter of the second high section 17 of the A zone is greater than the outer diameter of the second high section 17 of the B zone, so that the gap between the second high section 17 and the first rib 14 can be reduced, the bypass of the coolant can be reduced, the heat exchange between the coolant and the refrigerant can be improved, and the heat exchange effect of the heat exchanger 100 can be improved. In other embodiments, the outer diameter of the second high section 17 of the A zone can also be equal to or less than the outer diameter of the second high section 17 of the B zone.

[0237] Combination Figure 48-Figure 73The first inter-plate channel S1 includes a first sub-inter-plate channel S11, and the first sub-inter-plate channel S11 is located between the first rib 14 and the first convex portion 11. It should be noted that the first convex portion 11 here does not refer to a single convex portion, but a first convex portion group composed of a plurality of first convex portions 11 arranged side by side near the first rib 14 along the length direction of the plate 5. When the refrigerant flows into the first inter-plate channel S1 from the first channel 101, part of the refrigerant is diverted to the first sub-inter-plate channel S11. In the known technology, the first sub-inter-plate channel S11 has a small flow resistance, a fast flow rate, and a large relative flow volume compared to other first inter-plate channels S1 because there is no rib blocking it, which affects the heat exchange effect. In this embodiment, the first plate 15 includes a connecting portion 8, the connecting portion 8 is located between the first rib 14 and the above-mentioned first convex portion group, the connecting portion 8 protrudes toward the second plate 25 relative to the first substrate 35, and along the height direction of the heat exchanger 100, at least part of the first convex portion 11 is close to the second plate 25 relative to the connecting portion 8, that is, at least part of the first convex portion 11 is far away from the first substrate 35 of the first plate 15 relative to the connecting portion 8. The setting of the connecting portion 8 can relatively increase the flow resistance of the first sub-plate channel S11, increase the heat exchange area of ​​the first sub-plate channel S11, and improve the heat exchange efficiency. On the other hand, due to the setting of the connecting portion 8, when the refrigerant flows from the first channel 101 into the first inter-plate channel S1, the amount of refrigerant allocated to the first sub-plate channel S11 is relatively small, and the amount of refrigerant allocated to other first inter-plate channels S1 increases. As described in the above scheme, the first convex portion 11 includes a first high section 12 and a first low section 13, which improves the heat exchange performance.

[0238] Specifically, in the present embodiment, one end of the connecting portion 8 is connected to the first rib 14, and / or the other end of the connecting portion 8 is connected to the first protrusion 11. Of course, in some other embodiments, the connecting portion 8 is located between the first rib 14 and the first protrusion 11, and the two ends of the connecting portion 8 are not connected to the first rib 14 and the first protrusion 11.

[0239] In this embodiment, a plurality of connection parts 8 can be provided, and the plurality of connection parts 8 are arranged at intervals along the length direction of the heat exchanger 100. For better heat exchange effect, connection parts 8 are provided from the inflow area where the refrigerant enters the first inter-sub-plate channel S11 to the area where the refrigerant flows out of the first inter-sub-plate channel S11. Specifically, in this embodiment, the first rib 14 is in a Z-shaped wave shape, and the first rib 14 includes a first part 142 and a second part 143. The first part 142 and the second part 143 are alternately arranged along the length direction of the first rib 14, and the adjacent first part 142 and the second part 143 are connected. In this embodiment, the extension direction F of the first part 142 is parallel or substantially parallel, and the extension direction of the second part 143 is parallel or substantially parallel to the E direction. Such an arrangement can make the shape of the first rib 14 substantially the same as the flow direction of the refrigerant, avoid the first rib 14 from hindering the flow of the refrigerant, make the refrigerant flow more smoothly, and make the refrigerant and the coolant have a higher heat exchange effect. It should be noted that the above-mentioned substantially parallel means that the angle with the F direction and the E direction is 0-10 degrees. For the convenience of manufacturing and simple mold forming, some of the multiple connecting parts 8 are arranged along the F direction, and / or, some of the multiple connecting parts 8 are arranged along the E direction, wherein the connecting part 8 arranged along the F direction has one end connected to the first protrusion 11, and the other end connected to the second part 143 of the first rib 14; wherein the connecting part 8 arranged along the E direction has one end connected to the first protrusion 11, and the other end connected to the first part 142 of the first rib 14. It can be understood that the connecting part 8 connected to the first part 142 and the connecting part 8 connected to the second part 143 are symmetrically arranged, and the intersection line of the first part 142 and the second part 143 is parallel to the width direction of the heat exchanger 100. For the refrigerant side, due to the low viscosity of the refrigerant itself, when the refrigerant flows through the first inter-sub-plate channel S11, the setting of the connecting portion 8 can increase the flow resistance of the refrigerant. It can be understood that multiple connecting portions 8 are set, and some connecting portions 8 are set along the F direction, and some connecting portions 8 are set along the E direction, and the two are set alternately, and at least part of the first rib 14, the connecting portion 8, the first convex portion 11, the first substrate 35, and the second plate 25 define a low flow position, and the connecting portion 8 and part of the second plate 25 define a high flow position. Then, the refrigerant in the first inter-sub-plate channel S11 flows in a wavy path along the height direction of the heat exchanger 100, that is, a flow channel structure of "high flow position-low flow position-high flow position" is formed. Compared with the straight line without the connecting portion 8, the setting of the connecting portion 8 of this scheme can increase the flow resistance when the refrigerant flows, and the setting of the connecting portion 8 can also increase the heat exchange area between the fluids and improve the heat exchange performance.

[0240] Of course, in some other embodiments, the plurality of connection portions 8 are respectively connected to the first portion 142 of the first convex rib, or the plurality of connection portions 8 are respectively connected to the second portion 143 of the first convex rib.

[0241] In order to make the connection part 8 have a better effect, in this embodiment, along the length direction of the heat exchanger 100, the area where the connection part 8 is set occupies at least 1 / 4 of the length of the first rib, and the area where the connection part 8 is set is close to the first channel 101 for the inflow of the refrigerant.

[0242] Define the distance between the highest point of the first protrusion 11 and the first substrate 35 as T1, and the distance between the highest point of the connecting portion 8 and the first substrate 35 as T2, then T2=(0.3-0.7)T1.

[0243] During the manufacturing process, the first plate 15 and the second plate 25 are stacked and welded together. The fixing points of the first plate 15 and the second plate 25 are part of the first protrusion 11 of the first plate 15, part of the end of the first protrusion rib and the second substrate 36 of the second plate 25. During the welding process, in order to prevent the solder from blocking the flow channel above the connecting portion 8 during the flow, the distance T2 from the highest point of the connecting portion 8 to the first substrate 35 should be set within a certain range. In this way, the flow resistance of the first sub-board inter-channel S11 can be increased, which can ensure normal welding and prevent welding blockage.

[0244] In this solution, in order to improve the strength of the heat exchanger 100, reinforcing ribs 9 are provided on the plate 5. Specifically, Figure 64-Figure 65 As shown, the heat exchanger 100 has a reinforcing rib 9, which is located on the first plate 15, and the reinforcing rib 9 protrudes toward the second plate 25 relative to the first substrate 35, and the reinforcing rib 9 abuts against and is fixedly connected to the second plate 25; and / or, the reinforcing rib 9 is located on the second plate 25, and the reinforcing rib 9 protrudes toward the first plate 15 relative to the second substrate 36, and the reinforcing rib 9 abuts against and is fixedly connected to the first plate 15.

[0245] In this embodiment, the reinforcing rib 9 is located at the first plate 15 and / or the second plate 25. Along the width direction of the heat exchanger 100, when the reinforcing rib 9 displaces the first plate 15, the reinforcing rib 9 is located at the area of ​​the first substrate 35 close to the edge of the first substrate 35, that is, the reinforcing rib 9 is located between the flange 4 and the first convex portion 11, and the height of the reinforcing rib 9 from the first substrate 35 of the first plate 15 is the same as the height of the first convex portion 11 from the first substrate 35; when the reinforcing rib 9 is located at the second plate 25, one end of the reinforcing rib 9 abuts against the second plate 25 and is fixed by welding, and the height of the reinforcing rib 9 from the second substrate 36 is the same as the height of the second convex portion 201 from the second substrate 36. The provision of the reinforcing rib 9 helps to improve the strength of the heat exchanger 100 during welding.

[0246] It can be understood that multiple reinforcing ribs 9 can be provided, and the structure and shape of the reinforcing ribs 9 can be similar to the structure and shape of the second convex portion 201, or the reinforcing ribs 9 are bosses provided on the plate 5. Compared with the known technology, there is a plane area at the part of the convex portion on the plate 5 away from the edge of the plate 5. When the plates 5 are stacked, there is a gap in the plane area of ​​the plate 5 without structural support, and the strength here is relatively weakened. The provision of the reinforcing ribs 9 in this solution can improve the strength of this area, and the provision of the reinforcing ribs 9 plays a role of diversion to a certain extent.

[0247] The reinforcing rib 9 is located on the second plate 25, and along the height direction of the heat exchanger 100, the reinforcing rib 9 protrudes toward the first plate 15 located above the second plate 25 relative to the second substrate 36, and the reinforcing rib 9 abuts against the first substrate 35 of the first plate 15 and is welded and fixed; when the reinforcing rib 9 is located on the first plate 15, along the height direction of the heat exchanger 100, the reinforcing rib 9 protrudes toward the second plate 25 located above the first plate 15 relative to the first substrate 35, and the reinforcing rib 9 abuts against the second substrate 36 of the second plate 25 and is welded and fixed.

[0248] In some embodiments, the first plate 15 includes a first flow portion LT1, and the second plate 25 has a second flow portion LT2. Along the height direction of the heat exchanger 100, the first flow portion LT1 and the second flow portion LT2 are arranged opposite to each other; the second plate 25 has a welding portion 7, and the welding portion 7 is located at the second flow portion LT2. The welding portion 7 includes a first sub-welding portion 71 and a second sub-welding portion 72; the second plate 25 includes a second substrate 36. Along the height direction of the heat exchanger 100, the first sub-welding portion 71 and the second sub-welding portion 72 protrude outward in opposite directions relative to the second substrate 36. The first sub-welding portion 71 is fixedly connected to the first plate 15, and the second sub-welding portion 72 is fixedly connected to the other first plate 15. Specifically, the first flow portion LT1 includes a first plane portion LT11. Along the length direction of the heat exchanger 100, the first plane portion LT11 is located near the edge of the first plate 15. It can also be understood that along the width direction of the heat exchanger 100, the first plane portion LT11 is close to the inlet or outlet of the fluid; the second flow portion LT2 includes a second plane portion LT12, and the welding portion 7 is located at the second plane portion LT12.

[0249] It can be understood that, in the U-shaped flow channel, when the fluid enters the second inter-plate channel S2, if there is no plane portion, most of the fluid will turn and flow back through the end of the second rib 22, and the heat exchange path is shorter, which affects the heat exchange effect; the setting of the second plane portion LT12 can reduce the pressure drop of the fluid to a certain extent, reduce the pressure drop, reduce the flow resistance, and part of the fluid flows in the direction of the plane portion, which has a certain effect on the flow direction of the fluid and relatively improves the heat exchange effect. The setting of the welding portion 7, in addition to improving the welding strength between the first plate 15 and the second plate 25, also has the function of drainage distribution. When the fluid passes through the welding portion 7, part of the fluid does not pass through the welding portion 7 and directly turns and flows back, and part of the fluid bypasses the welding portion 7 and flows back, thereby improving the overall heat exchange performance.

[0250] The first sub-welding portion 71 protrudes toward the first plate 15 relative to the second substrate 36, and the second sub-welding portion 72 protrudes toward the other first plate 15, and the second sub-welding portion 72 is located at the periphery of the first sub-welding portion 71. Along the height direction of the heat exchanger 100, the first sub-welding portion 71 and the second sub-welding portion 72 are arranged opposite to each other. It can be understood that the first sub-welding portion 71 is a point portion, and the second sub-welding portion 72 is a ring portion. The second sub-welding portion 72 abuts against and is fixedly welded to the first circulation portion LT1 of the first plate 15, and the first sub-welding portion 71 abuts against and is fixedly welded to the first circulation portion LT1 of the other first plate 15. The setting of this welding portion 7 is conducive to enhancing the structural strength of the heat exchanger 100, and the welding portion 7 is welded and fixed to the adjacent first plate 15, which further increases the structural strength, and the structure of the welding portion 7 is simple.

[0251] It should be noted that: It should be noted that: the above embodiments are only used to illustrate the present application and are not intended to limit the technical solutions described in the present application. Although this specification has described the present application in detail with reference to the above embodiments, ordinary technicians in the field should understand that technicians in the relevant technical field can still modify or replace the application with equivalents, and all technical solutions and improvements that do not depart from the spirit and scope of the present application should be included in the scope of the claims of the present application.

Claims

1. A heat exchanger, characterized in that: The heat exchanger has a middle area and an end area. Along the length direction of the heat exchanger, the end areas are located on both sides of the middle area. The heat exchanger includes at least two plates stacked along the height direction of the heat exchanger. The heat exchanger has at least one inter-plate channel. The same inter-plate channels can flow the same fluid. The inter-plate channels are located between adjacent plates. The same inter-plate channels include at least two sub-channels arranged along the height direction of the heat exchanger. Among the same inter-plate channels, at least one sub-channel has a bypass flow channel, and the bypass flow channel is located in the end area.

2. The heat exchanger according to claim 1, characterized in that: The plate comprises a plurality of protruding structures, at least a portion of which are distributed in the middle area; In the same type of inter-plate channels, all the sub-channels have bypass channels, and the flow cross-sectional area of ​​the inter-plate channels located in the middle area is smaller than the flow cross-sectional area of ​​the bypass channels.

3. The heat exchanger according to claim 2, characterized in that: The plate comprises a main body and a flange, wherein the flange is an outer peripheral side surrounding the main body, a part of the main body is located in the middle area, and another part of the main body is located in the end area; The bypass flow channel includes a first flow channel, which extends along the width direction of the heat exchanger, and the extension distance of the first flow channel is less than or equal to the width of the main body, and / or the bypass flow channel includes a second flow channel, which extends along the length direction of the heat exchanger, and at least a portion of the second flow channel is located in the end area.

4. The heat exchanger according to claim 3, characterized in that The bypass flow channel includes a first flow channel and a second flow channel, the first flow channel is connected to the second flow channel, the second flow channel is entirely located in the end area, and the second flow channel is adjacent to the protruding structure.

5. The heat exchanger according to claim 1, characterized in that: The heat exchanger has a corner hole channel, which is connected to the same type of inter-plate channel. In the same type of inter-plate channel, the corner hole channel is located in one end zone, and the bypass flow channel is located in the other end zone.

6. The heat exchanger according to any one of claims 1 to 5, characterized in that: The inter-plate channel includes a first inter-plate channel and a second inter-plate channel, the first inter-plate channel and the second inter-plate channel are fluidically isolated, the sub-channel of the first inter-plate channel has a bypass flow channel, and the sub-channel of the second inter-plate channel has a bypass flow channel, the bypass flow channel of the first inter-plate channel is defined as a first bypass channel, and the bypass flow channel of the second inter-plate channel is defined as a second bypass channel, the first bypass channel is located at one end area of ​​the heat exchanger in the width direction, and the second bypass channel is located at the other end area of ​​the heat exchanger in the width direction.

7. The heat exchanger according to any one of claims 1 to 5, characterized in that: The plate includes a convex rib, the convex rib defines a portion of the wall of the inter-plate channel, the depth of the convex rib is the same as the depth of the bypass flow channel, the convex rib extends from an edge of one end region in the length direction of the plate to the other end region, or the convex rib extends from an edge of the wall defining the bypass flow channel to the other end region; The projection distance of the rib along the length direction of the plate is smaller than the length of the plate body.

8. The heat exchanger according to claim 7, characterized in that In the same inter-plate channel, a flow gap is provided between the rib and the end region away from the bypass flow channel; The middle zone includes a first sub-zone and a second sub-zone, the first sub-zone and the second sub-zone are arranged along the width direction of the heat exchanger, part of the ribs are located between the first sub-zone and the second sub-zone, and the inter-plate channel located in the first sub-zone and the inter-plate channel located in the second sub-zone are connected through the flow gap and the bypass channel.

9. The heat exchanger according to claim 7, characterized in that: The convex rib extends from the edge of one end region of the plate in the length direction to the other end region, the bypass flow channel includes a first flow channel, the first flow channel includes at least two parts, along the width direction of the heat exchanger, at least one part is located on one side of the convex rib, and at least one part is located on the other side of the convex rib; Alternatively, the bypass flow channel extends over the entire width of the heat exchanger, and the rib extends from an edge of a wall portion defining the bypass flow channel toward the other end region.

10. The heat exchanger according to claims 1 to 9, characterized in that The plates include a first plate and a second plate, and along the height direction of the heat exchanger, the first plate and the second plate are alternately stacked; The first plate comprises a first rib, a first substrate, a first convex portion, a first bypass structure and a first circulation portion, wherein the first rib extends along the length direction of the first plate, the first rib protrudes relative to the first substrate toward the second plate, the protruding direction of the first rib, the protruding direction of the first bypass structure and the first convex portion are consistent, the first bypass structure has a first bypass groove along the protruding direction away from the first rib, the wall surface of the first bypass groove defines the bypass flow channel, one end of the first rib is connected to one end of the first plate or to the first bypass structure, the first circulation portion is located between the other end of the first rib and the other end of the first plate, and there is a gap between the first circulation portion and the second plate along the height direction of the heat exchanger; And / or, the second plate comprises a second rib, a second base plate, a second convex portion, a second bypass structure and a second circulation portion, the second rib extends along the length direction of the second plate, the second rib protrudes relative to the second base plate toward the first plate, the second bypass structure has a second bypass groove, the wall surface of the second bypass groove defines the bypass flow channel, the protruding direction of the second rib, the protruding direction of the second bypass structure and the second convex portion are consistent, one end of the second rib and one end of the second plate are connected to the second bypass structure, the second circulation portion is located between the other end of the second rib and the other end of the second plate, and along the height direction of the heat exchanger, there is a gap between the second circulation portion and the first plate; The first plate includes a first rib portion, and the second plate includes a second rib portion. Projected along the height direction of the heat exchanger, the first rib portion and the second rib portion are staggered.

11. A heat exchanger, characterized in that: The heat exchanger has a middle area, and the heat exchanger includes at least two plates, and the plates are stacked along the height direction of the heat exchanger. The plates include a plurality of protrusion structures, and at least a portion of the protrusion structures are scattered in the middle area. The protrusion structures located in the middle area are arranged in an array along a first direction and a second direction. The first direction intersects with the second direction, and one of the angles between the first direction and the second direction is defined as α1, and α1 is toward the length direction of the heat exchanger, and α1 is less than 90 degrees.

12. The heat exchanger according to claim 11, characterized in that α1 is greater than or equal to 15 degrees and less than or equal to 75 degrees.

13. The heat exchanger according to claim 11 or 12, characterized in that: The heat exchanger further comprises end regions, along the length direction of the heat exchanger, wherein one end region is located on one side of the middle region, and the other end region is located on the other side of the middle region; A portion of the protruding structures are dispersed in at least one of the end regions, and the protruding structures located in the end region are arranged in an array along the first direction and the second direction.

14. The heat exchanger according to claim 11, characterized in that Another angle between the first direction and the second direction is defined as α2, wherein α2 is toward the width direction of the heat exchanger and α2 is greater than 90 degrees.

15. The heat exchanger according to claim 14, characterized in that The plate includes a first plate, the first plate includes a first substrate and a first protrusion connected to each other, the first protrusion protrudes from the first substrate in a direction away from the first substrate, the first protrusion has a first edge and a second edge, along the length direction of the heat exchanger, the angle α3 between the first edge and the second edge is less than 90 degrees, and / or in a first reference quadrilateral formed by connecting the center points of four adjacent first protrusions, along the length direction of the heat exchanger, one of the angles α4 of the first reference quadrilateral is less than 90 degrees.

16. The heat exchanger according to claim 15, characterized in that The first convex portion has a third edge and a fourth edge, and along the length direction of the heat exchanger, an angle α31 between the third edge and the fourth edge is less than 90 degrees, and / or in a first reference quadrilateral formed by connecting the center points of four adjacent first convex portions, along the length direction of the heat exchanger, another angle α41 of the first reference quadrilateral is less than 90 degrees; Along the width direction toward the heat exchanger, the angle α5 between the first edge and the fourth edge is greater than 90 degrees, and / or in a first reference quadrilateral formed by connecting the center points of four adjacent first protrusions, along the width direction toward the heat exchanger, another angle α6 of the first reference quadrilateral is greater than 90 degrees.

17. The heat exchanger according to claim 15, characterized in that The heat exchanger further has an end region, a part of the protrusion structures are distributed in at least one of the end regions, and in the first plate, at least a part of the protrusion structures located in the end region and the protrusion structures located in the middle region are of the same or similar pattern; Alternatively, for the raised structure located in the end area, in a second reference quadrilateral formed by connecting the center points of four adjacent first protrusions, along the length direction of the heat exchanger, an angle α7 of the second reference quadrilateral is less than 90 degrees, and along the width direction of the heat exchanger, an angle α8 of the second reference quadrilateral is greater than 90 degrees.

18. The heat exchanger according to claim 15, characterized in that The plate further includes a second plate, the first plate and the second plate are alternately stacked along the height direction of the heat exchanger, the heat exchanger has an inter-plate channel, and the inter-plate channel is located between the first plate and the second plate; The second plate includes a second substrate and a second protrusion that are connected to each other, and the second protrusion protrudes from the second substrate toward a direction away from the second substrate. In a second reference quadrilateral formed by connecting the center points of four adjacent second protrusions, along the length direction of the heat exchanger, the angle α9 of the third reference quadrilateral is less than 90 degrees, and along the width direction of the heat exchanger, the angle α10 of the third reference quadrilateral is greater than 90 degrees.

19. The heat exchanger according to claim 18, characterized in that The second plate further includes a low segment, the low segment is recessed relative to the second convex portion, the low segment is arranged in an array along the first direction and the second direction, and the low segment and the second convex portion are arranged alternately along the length direction and the width direction of the second plate; In the fourth reference quadrilateral formed by connecting the center points of the four adjacent low-level segments, along the length direction of the heat exchanger, the included angle α11 of the fourth reference quadrilateral is less than 90 degrees, and along the width direction of the heat exchanger, the included angle α12 of the fourth reference quadrilateral is greater than 90 degrees.

20. The heat exchanger according to claim 18, characterized in that The heat exchanger further has an end region, a part of the protrusion structures are distributed in at least one of the end regions, and in the second plate, the protrusion structures located in the end region and the protrusion structures located in the middle region are of the same or similar pattern; Alternatively, the protruding structure located in the end region is a rhombus-like structure.

21. A heat exchanger, comprising a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first base plate, wherein the first protrusions protrude relative to the first base plate toward the second plate; The first plate comprises a first rib portion, the first rib portion protrudes relative to the first substrate toward the second plate, and the protruding direction of the first rib portion is consistent with the protruding direction of the first protruding portion; The plurality of first protrusions include a first group of first protrusions and a second group of first protrusions, wherein the first group of first protrusions and the second group of first protrusions are both composed of first protrusions adjacent to the first ribs; A direction perpendicular to the extension direction of the first rib is defined as a third direction, along which the first group of first protrusions is located on one side of the first rib, and the second group of first protrusions is located on the other side of the first rib, and along which the first group of first protrusions is closer to the first rib than the second group of first protrusions.

22. A heat exchanger, comprising a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first base plate, wherein the first protrusions protrude relative to the first base plate toward the second plate; The first plate comprises a first rib portion, the first rib portion protrudes relative to the first substrate toward the second plate, and the protruding direction of the first rib portion is consistent with the protruding direction of the first protruding portion; The plurality of first protrusions include a first group of first protrusions and a second group of first protrusions, wherein the first group of first protrusions and the second group of first protrusions are both composed of first protrusions adjacent to the first ribs; A direction perpendicular to the extension direction of the first rib is defined as a third direction, along which the first group of first protrusions is located on one side of the first rib, and the second group of first protrusions is located on the other side of the first rib; along the third direction, a width of the first group of first protrusions is greater than a width of the second group of first protrusions.

23. A heat exchanger, characterized in that: It includes a first plate and a second plate, with a first inter-plate channel between the first plate and the second plate, and is characterized in that the first plate includes a first rib, the first rib protrudes toward the second plate, the first rib extends in a curved shape along the length direction of the first plate, and the first rib and the plate surface of the second plate are welded and fixed.

24. A heat exchanger, characterized in that: It includes a first plate and a second plate, with a first inter-plate channel between the first plate and the second plate, the first plate includes a first rib, the first rib protrudes toward the second plate, the first rib and the plate surface of the second plate are welded and fixed, the first plate includes a first protrusion, the first protrusion protrudes toward the second plate; the first protrusion is arranged along the F direction, and part of the first rib extends parallel to the F direction.

25. A heat exchanger, comprising a first plate, characterized in that: The first plate includes a first substrate and a plurality of first high segments, wherein the first high segments are protruded relative to the first substrate, and along the width direction of the heat exchanger, the distance between the center points of two adjacent first high segments is d1, and the ratio of d1 to the height H2 of the top of the first high segment from the plate surface of the first substrate is 1.5 to 6.

26. A plate, characterized in that: The invention comprises a rib portion, wherein the rib portion protrudes from the plate, and extends from one side of the plate to the other opposite side along the length direction of the plate, and a connecting portion is provided between the rib portion and one side of the plate along the extending direction of the rib portion, and the plate comprises an angular hole, and along the length direction of the plate, the angular hole is close to the other side of the plate relative to the connecting portion.

27. A heat exchanger, characterized in that: It comprises a plurality of plates as described in claim 1, wherein the plurality of plates are stacked, wherein a first inter-plate channel or a second inter-plate channel is provided between the plates and adjacent plates, wherein the ribs abut against adjacent plates, wherein the connecting portions connect areas on both sides of the ribs, and wherein the connecting portions on both sides of the plates at least partially overlap.

28. A heat exchanger, characterized in that: The invention comprises a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first substrate, and wherein the first protrusions protrude relative to the first substrate toward the second plate; The first plate includes a first rib and a connecting portion, wherein the first rib is located on the first substrate. Along the length direction of the heat exchanger, the first rib extends from one end of the first plate to the other end, and the connecting portion is located between the first rib and the first protrusion. The connecting portion protrudes toward the second plate relative to the first substrate. Along the height direction of the heat exchanger, at least part of the first protrusion is close to the second plate relative to the connecting portion.

29. A heat exchanger, characterized in that: The invention comprises a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first substrate, wherein the first protrusions protrude relative to the first substrate toward the second plate, and wherein the second plate comprises a second substrate and a plurality of second protrusions; The heat exchanger has a reinforcing rib, which is located on the first plate, protrudes toward the second plate relative to the first substrate, and abuts against and is fixedly connected to the second plate; and / or, the reinforcing rib is located on the second plate, protrudes toward the first plate relative to the second substrate, and abuts against and is fixedly connected to the first plate.

30. A heat exchanger, characterized in that: The first plate includes a first circulation portion, and the second plate includes a second circulation portion, and the first circulation portion and the second circulation portion are arranged opposite to each other along the height direction of the heat exchanger; the second plate includes a welding portion, and the welding portion is located at the second circulation portion, and the welding portion includes a first sub-welding portion and a second sub-welding portion; the second plate includes a second base plate, and along the height direction of the heat exchanger, the first sub-welding portion and the second sub-welding portion protrude outward in opposite directions relative to the second base plate, and the first sub-welding portion is fixedly connected to the first plate, and the second sub-welding portion is fixedly connected to another first plate.

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